JPWO2013105147A1 - Vane type compressor - Google Patents

Abstract

A vane compressor that suppresses wear at the tip of the vane, supports the rotating shaft portion with a small diameter, reduces bearing sliding loss, and improves the outer diameter of the rotor portion and the accuracy of the rotation center is obtained. The clearance between the vane tip 5b and the cylinder inner peripheral surface 1b is δ, the radius of the cylinder inner peripheral surface 1b is rc, the radius of the vane aligner bearing portions 2b and 3b is ra, and the equation rv = rc−ra−δ Thus, by setting the distance rv between the outer peripheral side of the vane aligner portions 5c and 5d and the vane tip portion 5b, the vane tip portion 5b of the first vane 5 does not contact the cylinder inner peripheral surface 1b. Will rotate.

Description

  The present invention relates to a vane type compressor.

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

  The rotor shaft has a hollow interior and a vane fixed shaft disposed therein. The vane is rotatably attached to the fixed shaft, and a pair of semicircular rods is formed near the outer periphery of the rotor portion. There has been proposed a vane type compressor in which a vane is rotatably held with respect to a rotor part via a clamping member (bush) (see, for example, Patent Document 2).

JP-A-10-252675 (page 4, FIG. 1) JP 2000-352390 A (6th page, FIG. 1)

  In the conventional general vane type compressor described in Patent Document 1, since the curvature radius of the vane tip and the curvature radius of the inner circumferential surface of the cylinder are greatly different, the oil film is not formed between the inner circumferential surface of the cylinder and the vane tip. It is not formed, and it slides in a boundary lubrication state instead of a fluid lubrication state. In general, the friction coefficient in the lubrication state is about 0.001 to 0.005 in the fluid lubrication state, but becomes very large in the boundary lubrication state, and is generally about 0.05 or more.

  For this reason, in the configuration of a conventional general vane type compressor, sliding resistance increases due to sliding between the tip of the vane and the inner peripheral surface of the cylinder in the boundary lubrication state, and compressor efficiency due to an increase in mechanical loss. There has been a problem in that a significant decrease in the amount of occurrence occurs. At the same time, 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.

  Therefore, to improve the above-mentioned problems, the interior of the rotor part is made hollow, and a vane is rotatably supported at the center of the inner peripheral surface of the cylinder, and the vane is a rotor. A method of holding a vane via a clamping member in the vicinity of the outer peripheral portion of the rotor portion so as to be rotatable with respect to the portion (for example, Patent Document 2 above) has been proposed.

  With this configuration, the vane is rotatably supported at the center of the inner peripheral surface of the cylinder. Thereby, 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 cylinder inner peripheral surface. 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 due to sliding at the vane tip occurs, A vane type compressor capable of suppressing wear on the inner peripheral surface of the cylinder can be obtained.

  However, in the method described in Patent Document 2, it is difficult to apply a rotational force to the rotor portion and to support the rotation of the rotor portion by forming the hollow inside the rotor portion. Moreover, in patent document 2, the end plate is provided in the both end surfaces of the rotor part. The end plate on one side has a disk shape because it is necessary to transmit power from the rotating shaft, and the rotating shaft is connected to the center of the end plate. Moreover, since it is necessary to comprise the end plate of the other side so that it may not interfere with the rotation range of a vane fixed axis | shaft and a vane axis | shaft support material, it is necessary to comprise in the ring shape which opened the hole in the center part. For this reason, the part which supports the end plate in rotation needs to be configured to have a larger diameter than that of the rotating shaft, and there is a problem that bearing sliding loss increases.

  Further, since a narrow gap is formed between the rotor portion and the inner peripheral surface of the cylinder so that the compressed gas does not leak, the outer diameter and the rotation center portion of the rotor portion are required to have high accuracy. However, since the rotor part and the end plate are composed of separate parts, the outer diameter of the rotor part, such as the distortion generated by the fastening of the rotor part and the end plate, and the coaxial displacement between the rotor part and the end plate, etc. There is also a problem that the accuracy of the rotation center portion is deteriorated.

  The present invention has been made in order to solve the above-described problems, and can suppress wear of the tip of the vane, reduce the bearing sliding loss by being able to support the rotating shaft portion with a small diameter, and reduce the rotor portion. An object of the present invention is to obtain a vane type compressor that improves the accuracy of the outer diameter and the rotation center.

  A vane compressor according to the present invention includes a cylinder having a cylindrical inner peripheral surface, and a cylinder that rotates around a rotation axis that is deviated from the central axis of the inner peripheral surface by a predetermined distance inside the cylinder. A rotor shaft having a shape, and a rotor shaft having a rotation shaft portion for transmitting a rotational force to the rotor portion, and one opening portion of the inner peripheral surface of the cylinder is closed, and the rotation shaft is moved by a main bearing portion. A frame to be supported; a cylinder head that closes the other opening of the inner peripheral surface of the cylinder and supports the rotating shaft by a main bearing; and a tip that is provided on the rotor and protrudes from the rotor A vane-type compressor comprising: at least one vane formed in an arc shape protruding outward, wherein the arc-shaped normal line of the tip of the vane and the cylinder The vane is supported so that the refrigerant is compressed in a space surrounded by the vane, the outer peripheral portion of the rotor portion, and the inner peripheral surface of the cylinder in a state where the normal line of the inner peripheral surface of the cylinder always coincides with the normal line. And vane support means for supporting the vane so as to be rotatable and movable with respect to the rotor portion, wherein the rotor shaft is formed by integrally forming the rotor portion and the rotary shaft portion, and the vane The radius of curvature of the arc shape of the tip of the cylinder is substantially the same as the radius of curvature of the inner peripheral surface of the cylinder, and the vane support means is located in the vicinity of the outer peripheral portion of the rotor portion and the central axis of the rotor portion. A bush holding portion penetrating in the direction of the central axis so that a cross section perpendicular to the direction is substantially circular, and a pair of substantially semi-cylindrical objects inserted into the bush holding portion, the bush In the rotor portion, the rotor is arranged such that a bush for sandwiching the vane in the holding portion and an end surface on the inner peripheral surface center side which is the center of the inner peripheral surface of the cylinder in the vane do not contact the rotor portion. A vane relief portion formed so as to penetrate in the central axis direction of the portion, and the vane is near the end surface on the frame side and the center side of the rotor portion, and on the cylinder head side and on the rotor portion. A pair of arc-shaped vane aligner portions provided near the end surface on the center side are formed, and concavities or grooves concentric with the inner peripheral surface of the cylinder are formed on the cylinder-side end surfaces of the frame and the cylinder head. The vane aligner is fitted into the recess or the groove, and is a vane aligner that is an outer peripheral surface of the recess or the groove. -A flat part perpendicular to the length direction of the vane is formed on the surface of the vane at the front end part side, which is supported by the bearing part.

According to the present invention, by providing a predetermined appropriate gap between the tip portion of the vane and the inner peripheral surface of the cylinder, the compressor efficiency due to an increase in mechanical loss while suppressing the leakage of the refrigerant from the tip portion. Can be suppressed, and wear at the tip can be reduced to zero.
In addition, the mechanism that the vane necessary to perform the compression operation so that the arc shape of the tip of the vane and the normal line of the inner peripheral surface of the cylinder always coincide substantially rotates around the center of the inner peripheral surface of the cylinder. Can be realized with a configuration in which the rotor portion and the rotating shaft portion are integrated, so that the rotating shaft portion can be supported with a small diameter, thereby reducing bearing sliding loss and improving the accuracy of the outer diameter of the rotor portion and the rotation center. It is possible to reduce the leakage loss by forming a narrow gap between the rotor portion and the inner peripheral surface of the cylinder.
In addition, by forming the flat portion in the vane aligner portion, it is possible to avoid the rotating grindstone from interfering with the vane aligner portion when the upper and lower end surfaces of the vane are polished. As a result, the gaps between the vane, the frame, and the cylinder head can be kept small, so that each sliding loss between the vane, the frame, and the cylinder head can be suppressed, and seizure resistance can be reduced. In addition to improving wear resistance, high efficiency can be realized.

It is a longitudinal cross-sectional view of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is a disassembled perspective view of the compression element 101 of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is the top view and front view of the 1st vane 5 and the 2nd vane 6 of the vane type compressor 200 which concern on Embodiment 1 of this invention. FIG. 2 is a cross-sectional view taken along the line II of FIG. 1 in the vane type compressor 200 according to Embodiment 1 of the present invention. It is a figure which shows the compression operation | movement of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is JJ sectional drawing in FIG. 1 which shows rotation operation | movement of the vane aligner parts 5c and 6c of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is principal part sectional drawing around the vane part 5a of the 1st vane 5 of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is a disassembled perspective view of the compression element 101 of another form of the vane type compressor 200 which concerns on Embodiment 1 of this invention. It is a figure which shows the flow in the micro clearance gap between the two solid surfaces which carry out relative motion in Embodiment 2 of this invention. It is the schematic diagram which showed the relationship between the vane aligner part 5c and the vane aligner bearing part 2b of the vane type compressor 200 which concerns on Embodiment 2 of this invention. It is an analysis model in Embodiment 2 of this invention. It is a figure which shows the state which the vane aligner part 5c fitted in the vane aligner bearing part 2b in the vane type compressor 200 which concerns on Embodiment 2 of this invention. It is the analysis result figure which showed the relationship between the Sommerfeld number S and (beta) / (alpha) in the case of the eccentricity (epsilon) = 0.9 in the vane type compressor 200 which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
1 is a longitudinal sectional view of a vane type compressor 200 according to Embodiment 1 of the present invention, FIG. 2 is an exploded perspective view of a compression element 101 of the vane type compressor 200, and FIG. These are the top view and front view of the 1st vane 5 and the 2nd vane 6 of the vane type compressor 200. Among these, in FIG. 1, an arrow indicated by a solid line indicates a flow of gas (refrigerant), and an arrow indicated by a broken line indicates a flow of refrigerating machine oil 25. Hereinafter, the structure of the vane type compressor 200 will be described with reference to FIGS.

  A vane type compressor 200 according to the present embodiment is located in a hermetic container 103 forming an outer shape, a compression element 101 accommodated in the hermetic container 103, and an upper part of the compression element 101, and drives the compression element 101. The electric element 102 and an oil sump 104 that stores the refrigerating machine oil 25 are provided at the bottom in the sealed container 103.

  The hermetic container 103 forms the outer shape of the vane compressor 200, and houses the compression element 101 and the electric element 102 therein, and hermetically seals the refrigerant and the refrigerating machine oil. A suction pipe 26 for sucking the refrigerant into the sealed container 103 is installed on the side surface of the sealed container 103, and a discharge pipe 24 for discharging the compressed refrigerant to the outside is installed on the upper surface of the sealed container 103. Yes.

  The compression element 101 compresses the refrigerant sucked into the sealed container 103 from the suction pipe 26, and includes the cylinder 1, the frame 2, the cylinder head 3, the rotor shaft 4, the first vane 5, the second vane 6, and , Bushes 7 and 8.

  The overall shape of the cylinder 1 is substantially cylindrical, and a substantially circular penetrating portion 1f is formed so that the position eccentric from the center of the cylindrical circle in the axial direction is the center. Further, a notch 1c that is wound in an R shape from the center of the penetrating portion 1f to the outside is provided on a part of the cylinder inner peripheral surface 1b that is the inner peripheral surface of the penetrating portion 1f. A suction port 1a is opened at 1c. The suction port 1a communicates with the suction pipe 26, and the refrigerant is sucked into the through portion 1f from the suction port 1a. Further, a discharge port 1d is cut out and provided on the opposite side of the suction port 1a with a nearest contact point 32, which will be described later, between the nearest contact point 32 and the side facing the frame 2 described later ( (See FIG. 2). Further, two oil return holes 1e are provided in the outer peripheral portion of the cylinder 1 in the axial direction and at positions symmetrical to the center of the through portion 1f.

  The frame 2 has a substantially T-shaped vertical cross section, and a portion in contact with the cylinder 1 has a substantially disk shape, and closes one opening (upper side in FIG. 2) of the through portion 1f of the cylinder 1. . The central portion of the frame 2 has a cylindrical shape. The cylindrical portion is hollow, and a main bearing portion 2c is formed here. Further, a concave portion 2a whose outer peripheral surface is concentric with the cylinder inner peripheral surface 1b is formed on the end surface of the frame 2 on the cylinder 1 side and the main bearing portion 2c. 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 fitted into the recess 2a. At this time, the vane aligner portions 5c and 6c are supported by the vane aligner bearing portion 2b which is the outer peripheral surface of the recess 2a. The frame 2 is provided with a discharge port 2d that communicates with a discharge port 1d provided in the cylinder 1 and penetrates in the axial direction. A discharge valve 2d is provided at an opening on the opposite side of the cylinder 1 from the discharge port 2d. 27 and a discharge valve presser 28 for restricting the opening degree of the discharge valve 27 are attached.

  The cylinder head 3 has a substantially T-shaped longitudinal cross-section, and the portion in contact with the cylinder 1 has a substantially disk shape, and closes the other opening (the lower side in FIG. 2) of the penetrating portion 1f of the cylinder 1. It is. Further, the central portion of the cylinder head 3 has a cylindrical shape, and this cylindrical shape is hollow, and a main bearing portion 3c is formed here. Further, a concave portion 3a whose outer peripheral surface is concentric with the cylinder inner peripheral surface 1b is formed on the end surface of the cylinder head 3 on the cylinder 1 side and the main bearing portion 3c. 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 fitted into the recess 3a. At this time, the vane aligner portions 5d and 6d are supported by the vane aligner bearing portion 3b which is the outer peripheral surface of the recess 3a.

  The rotor shaft 4 is a substantially cylindrical rotor portion 4a that rotates on a central axis that is eccentric from the central axis of the through-hole 1f of the cylinder 1 in the cylinder 1, and from the center of a circle that is the upper surface of the rotor portion 4a. The rotating shaft portion 4b extending vertically upward on the upper surface and the rotating shaft portion 4c extending vertically downward on the lower surface from the center of the circle that is the lower surface of the rotor portion 4a are integrated. ing. The rotation shaft portion 4 b is inserted and supported by the main bearing portion 2 c of the frame 2, and the rotation shaft portion 4 c is inserted and supported by the main bearing portion 3 c of the cylinder head 3. The rotor portion 4a has a substantially circular cross section perpendicular to the axial direction of the cylindrical rotor portion 4a and penetrates in the axial direction to form bush holding portions 4d and 4e and vane relief portions 4f and 4g. . The bush holding portions 4d and 4e are formed at positions that are symmetrical with respect to the center of the rotor portion 4a, and vane relief portions 4f and 4g are formed in the inner directions of the bush holding portions 4d and 4e, respectively. Yes. That is, the centers of the rotor portion 4a, the bush holding portions 4d and 4e, and the vane relief portions 4f and 4g are formed so as to be substantially linearly arranged. The bush holding portion 4d and the vane escape portion 4f communicate with each other, and the bush holding portion 4e and the vane escape portion 4g communicate with each other. Further, the axial end portions of the vane relief portions 4 f and 4 g communicate with the concave portion 2 a of the frame 2 and the concave portion 3 a of the cylinder head 3. Moreover, the oil pump 31 using the centrifugal force of the rotor shaft 4 as described in, for example, Japanese Patent Application Laid-Open No. 2009-264175 is provided at the lower end portion of the rotating shaft portion 4c of the rotor shaft 4. The oil pump 31 is provided at the shaft center portion at the lower end of the rotating shaft portion 4c of the rotor shaft 4 and extends upward from the lower end of the rotating shaft portion 4c to the inside of the rotor portion 4a and the rotating shaft portion 4b. It communicates with 4h. The rotary shaft portion 4b is provided with an oil supply passage 4i that allows the oil supply passage 4h to communicate with the recess 2a, and the rotation shaft portion 4c is provided with an oil supply passage 4j that allows the oil supply passage 4h to communicate with the recess 3a. . Furthermore, an oil drain hole 4k that communicates with the internal space of the sealed container 103 is provided at a position above the main bearing portion 2c of the rotary shaft portion 4b.

  The first vane 5 has a vane portion 5a, which is a substantially square plate-shaped member, an arc shape provided on the upper end surface of the vane portion 5a on the frame 2 side and the rotating shaft portion 4b side, that is, a partial ring shape. The vane aligner portion 5c and the vane aligner portion 5d having a circular arc shape, that is, a partial ring shape, provided on the lower end surface of the vane portion 5a on the cylinder head 3 side and the rotating shaft portion 4c side. The vane tip 5b, which is the end surface of the vane portion 5a on the cylinder inner peripheral surface 1b side, is formed in an outwardly convex arc shape, and the radius of curvature of the arc shape is substantially the same as the radius of curvature of the cylinder inner peripheral surface 1b. It is formed to be the same. Further, as shown in FIG. 3, the first vane 5 has the length direction of the vane portion 5a and the normal direction of the arc of the vane tip portion 5b passing through the center of the arc of the vane aligner portions 5c and 5d. Is formed. In addition, a flat surface portion 5e perpendicular to the length direction of the vane portion 5a is formed on the surface on the vane tip portion 5b side of the arc-shaped vane aligner portion 5c. Similarly, a flat surface portion 5f perpendicular to the length direction of the vane portion 5a is formed on the surface on the vane tip portion 5b side of the arc-shaped vane aligner portion 5d.

  The second vane 6 has a vane portion 6a, which is a substantially square plate-shaped member, an arc shape provided on the upper end surface of the vane portion 6a on the frame 2 side and the rotating shaft portion 4b side, that is, a partial ring shape. The vane aligner portion 6c and the vane aligner portion 6d having an arc shape, that is, a partial ring shape, provided on the lower end surface of the vane portion 6a on the cylinder head 3 side and the rotating shaft portion 4c side. The vane tip 6b, which is the end surface of the vane portion 6a on the cylinder inner peripheral surface 1b side, is formed in an outwardly convex arc shape, and the radius of curvature of the arc shape is substantially the same as the radius of curvature of the cylinder inner peripheral surface 1b. It is formed to be the same. Further, as shown in FIG. 3, the second vane 6 has a length direction of the vane portion 6a and a normal direction of the arc of the vane tip portion 6b passing through the centers of the arcs of the vane aligner portions 6c and 6d. Is formed. In addition, a flat surface portion 6e perpendicular to the length direction of the vane portion 6a is formed on the surface of the arc-shaped vane aligner portion 6c on the vane tip portion 6b side. Similarly, a flat surface portion 6f perpendicular to the length direction of the vane portion 6a is formed on the surface on the vane tip portion 6b side of the arc-shaped vane aligner portion 6d.

  The bushes 7 and 8 are each composed of a pair of objects formed in a substantially semi-cylindrical shape. The bush 7 is fitted into the bush holding portion 4 d of the rotor shaft 4, and a plate-shaped vane portion 5 a is sandwiched between the pair of bushes 7. At this time, the vane portion 5a is held so as to be rotatable with respect to the rotor portion 4a and movable in the length direction of the vane portion 5a. The bush 8 is fitted into the bush holding portion 4 e of the rotor shaft 4, and a plate-shaped vane portion 6 a is sandwiched between the pair of bushes 8. At this time, the vane portion 6a is held so as to be rotatable with respect to the rotor portion 4a and movable in the length direction of the vane portion 5a.

  The electric element 102 is composed of, for example, a brushless DC motor, and as shown in FIG. 1, the stator 21 fixed to the inner periphery of the hermetic container 103 and the inner side of the stator 21. It is comprised by the rotor 22 formed by these. Electric power is supplied to the stator 21 from a glass terminal 23 fixed to the upper surface of the hermetic container 103, and the rotor 22 is rotationally driven by this electric power. The rotor 22 is fixed with the rotating shaft portion 4b of the rotor shaft 4 described above. The rotating force of the rotor 22 is transmitted to the rotating shaft portion 4b when the rotor 22 is rotated. The entire shaft 4 is rotationally driven.

(Compression operation of the vane compressor 200)
4 is a cross-sectional view taken along the line II of FIG. 1 in the vane compressor 200 according to Embodiment 1 of the present invention, and FIG. 5 is a diagram illustrating a compression operation of the vane compressor 200. Hereinafter, the compression operation of the vane type compressor 200 will be described with reference to FIGS. 4 and 5.

  FIG. 4 shows a state in which the rotor portion 4a of the rotor shaft 4 is in closest contact with one place (the closest contact point 32) of the cylinder inner peripheral surface 1b. Here, when the radius of the vane aligner bearing portions 2b and 3b is ra (see FIG. 6 described later) and the radius of the cylinder inner peripheral surface 1b is rc, the outer periphery of the vane aligner portions 5c and 5d of the first vane 5 A distance rv (see FIG. 3) between the side and the vane tip 5b is expressed by the following equation (1).

  rv = rc-ra-δ (1)

  Here, δ represents the gap between the vane tip 5b and the cylinder inner peripheral surface 1b. By setting rv as shown in Equation (1), the vane tip 5b of the first vane 5 is It will rotate without contacting the cylinder inner peripheral surface 1b. Here, if rv is set so that δ is as small as possible, refrigerant leakage from the vane tip 5b is minimized. Further, the relationship of the expression (1) is the same for the second vane 6, and the second vane 6 rotates while maintaining a narrow gap between the vane tip 6 b of the second vane 6 and the cylinder inner peripheral surface 1 b. Will be.

  With the above configuration, the closest contact point 32 that is close to the cylinder inner peripheral surface 1b, the vane tip 5b of the first vane 5, and the vane tip 6b of the second vane 6 have 3 Two spaces (suction chamber 9, intermediate chamber 10 and compression chamber 11) are formed. The refrigerant sucked from the suction pipe 26 enters the suction chamber 9 through the suction port 1a of the notch 1c. As shown in FIG. 4 (the position of the rotation angle of the rotor shaft 4 is 90 °), the notch 1c is formed near the vane tip 5b of the first vane 5 and the inside of the cylinder from the vicinity of the closest point 32. It is formed up to the range of the proximity point A with the peripheral surface 1b. The compression chamber 11 communicates with the discharge port 2d provided in the frame 2 that is closed by the discharge valve 27 through the discharge port 1d of the cylinder 1 except when the refrigerant is discharged. Accordingly, the intermediate chamber 10 is a space formed in a rotation angle range that communicates with the suction port 1a up to a rotation angle of 90 °, but does not communicate with either the suction port 1a or the discharge port 1d, and thereafter the discharge port. The compression chamber 11 is communicated with 1d. In FIG. 4, bush centers 7a and 8a are the rotation centers of the bushes 7 and 8, respectively, and the rotation centers of the vane portions 5a and 6a.

Next, the rotation operation of the rotor shaft 4 of the vane type compressor 200 will be described.
The rotating shaft portion 4 b of the rotor shaft 4 receives the rotational force from the rotor 22 of the electric element 102, and the rotor portion 4 a rotates within the through portion 1 f of the cylinder 1. As the rotor portion 4 a rotates, the bush holding portions 4 d and 4 e of the rotor portion 4 a move on the circumference of a circle centered on the center of the rotor shaft 4. The pair of bushes 7 and 8 held in the bush holding portions 4d and 4e, respectively, and the vane portion 5a of the first vane 5 that is rotatably held between the pair of bushes 7 and 8 respectively. And the vane part 6a of the 2nd vane 6 also rotates with rotation of the rotor part 4a. The first vane 5 and the second vane 6 receive a centrifugal force due to the rotation of the rotor portion 4a, and the vane aligner portions 5c, 6c and the vane aligner portions 5d, 6d are slid by being pressed against the vane aligner bearing portions 2b, 3b, respectively. While moving, the vane aligner bearing portions 2b and 3b rotate around the center of rotation. Here, since the vane aligner bearing portions 2b and 3b and the cylinder inner peripheral surface 1b are concentric, 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 are respectively connected to the bush holding portions 4d, so that the length directions of the vane portion 5a of the first vane 5 and the vane portion 6a of the second vane 6 pass through the center of the cylinder inner peripheral surface 1b. Within 4e, the bush centers 7a and 8a are rotated about the rotation center. That is, the rotor portion 4a rotates in a state in which the arc shape of the vane tip portions 5b and 6b and the normal line of the cylinder inner peripheral surface 1b are always substantially matched.

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

  Next, how the volumes of the suction chamber 9, the intermediate chamber 10, and the compression chamber 11 change will be described with reference to FIG. In FIG. 5, for the sake of simplicity, illustration of the suction port 1a, the notch 1c, and the discharge port 1d is omitted, and the suction port 1a and the discharge port 1d are shown as suction and discharge by arrows, respectively. First, as the rotor shaft 4 rotates, low-pressure gas refrigerant flows from the suction port 1a via the suction pipe 26. Here, the rotation angle in FIG. 5 is the closest point 32 where the rotor portion 4a of the rotor shaft 4 and the cylinder inner peripheral surface 1b are closest to each other, and one location where the vane portion 5a and the cylinder inner peripheral surface 1b face each other. Are defined as “angle 0 °”. In FIG. 5, the positions of the vane part 5a and the vane part 6a in the case of “angle 0 °”, “angle 45 °”, “angle 90 °”, and “angle 135 °”, and the suction chamber 9 in each case, The state of the intermediate chamber 10 and the compression chamber 11 is shown. Further, in the “angle 0 °” diagram of FIG. 5, the rotation direction of the rotor shaft 4 (clockwise in FIG. 5) is indicated by an arrow. However, in the figures at other angles, the arrow indicating the rotation direction of the rotor shaft 4 is omitted. The state after “angle 180 °” is not shown when “angle 180 °” is the same as the state in which the first vane 5 and the second vane 6 are switched at “angle 0 °” Thereafter, the same compression operation as that from “angle 0 °” to “angle 135 °” is shown.

  In “angle 0 °” in FIG. 5, the right space partitioned by the closest contact 32 and the vane portion 6a of the second vane 6 is the intermediate chamber 10, and communicates with the suction port 1a via the notch portion 1c. And inhales the gas refrigerant. The left space partitioned by the closest contact 32 and the vane portion 6a of the second vane 6 becomes the compression chamber 11 communicating with the discharge port 1d.

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

  At the “angle of 90 °” in FIG. 5, the vane tip 5b of the first vane 5 overlaps with the proximity point A on the cylinder inner peripheral surface 1b, so that the intermediate chamber 10 does not communicate with the suction port 1a. Thereby, the suction of the gas refrigerant into 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 pressure of the gas refrigerant increases. The volume of the suction chamber 9 is larger than that at the “angle 45 °” and communicates with the suction port 1a through the notch 1c to suck the gas refrigerant.

  At “angle 135 °” in FIG. 5, the volume of the intermediate chamber 10 becomes smaller than that at “angle 90 °”, and the refrigerant pressure rises. Further, the volume of the compression chamber 11 becomes smaller than that at the “angle 90 °”, and the pressure of the refrigerant rises. Since the volume of the suction chamber 9 becomes larger than that at the “angle of 90 °”, the suction of the gas refrigerant is continued.

  Thereafter, the vane portion 6a of the second vane 6 approaches the discharge port 1d, but when the pressure of the gas refrigerant 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. Then, the gas refrigerant in the compression chamber 11 passes through the discharge port 1d and the discharge port 2d and is discharged into the sealed container 103 as shown in FIG. The gas 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) through the discharge pipe 24 fixed to the upper part of the sealed container 103. Therefore, the pressure in the sealed container 103 is a high discharge pressure.

  Further, when the vane portion 6a of the second vane 6 passes through the discharge port 1d, a little high-pressure gas refrigerant remains (loss) in the compression chamber 11. When the compression chamber 11 disappears at an “angle of 180 °” (not shown), the high-pressure gas refrigerant changes to a low-pressure gas 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 thereafter, the above compression operation is repeated.

  As described above, the volume of the suction chamber 9 gradually increases due to the rotation of the rotor portion 4a of the rotor shaft 4, and the suction of the gas refrigerant is continued. Thereafter, the suction chamber 9 moves to the intermediate chamber 10, but gradually (until the vane portion (the vane portion 5a or the vane portion 6a) separating the suction chamber 9 and the intermediate chamber 10 faces the proximity point A). The volume increases and the suction of the gas refrigerant is continued. In the middle of the process, the volume of the intermediate chamber 10 becomes maximum, and the communication with the suction port 1a is lost. Thus, the suction of the gas refrigerant is finished here. Thereafter, the volume of the intermediate chamber 10 gradually decreases, and the gas refrigerant is compressed. Thereafter, the intermediate chamber 10 moves to the compression chamber 11 and the compression of the gas refrigerant is continued. The gas refrigerant 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.

6 is a cross-sectional view taken along the line JJ in FIG. 1 illustrating the rotation operation of the vane aligner portions 5c and 6c of the vane type compressor 200 according to Embodiment 1 of the present invention. In the “angle 0 °” diagram of FIG. 6, the rotation direction of the vane aligner portions 5c and 6c (clockwise in FIG. 6) is indicated by an arrow. However, in the figures at other angles, the arrows indicating the rotation directions 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 about the center of the cylinder inner peripheral surface 1b. Accordingly, as shown in FIG. 6, the vane aligner portions 5c and 6c are supported by the vane aligner bearing portion 2b in the recess 2a and rotate around the center of the cylinder inner peripheral surface 1b. Similarly, the vane aligner portions 5d and 6d are supported by the vane aligner bearing portion 3b in the recess 3a and rotate around the center of the cylinder inner peripheral surface 1b.

(Behavior of refrigeration oil 25)
In the above operation, as shown in FIG. 1, the refrigerating machine oil 25 is sucked up from the oil sump 104 by the oil pump 31 by the rotation of the rotor shaft 4, and sent out to the oil supply path 4h. The refrigerating machine oil 25 sent out to the oil supply passage 4h is sent out to the recess 2a of the frame 2 through the oil supply passage 4i and to the recess 3a of the cylinder head 3 through 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 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 2a and 3a is supplied to the main bearing portion 2c of the frame 2 and the main bearing portion 3c of the cylinder head 3 to be lubricated.

FIG. 7 is a cross-sectional view of a main part around the vane portion 5a of the first vane 5 of the vane type compressor 200 according to Embodiment 1 of the present invention.
As shown in FIG. 7, the solid line arrows indicate the flow of the refrigerating machine oil 25. Since the pressure in the vane relief portion 4f is the discharge pressure and is higher than the pressure in 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. Further, a part of the refrigerating machine oil 25 sent out 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.

In the above description, the space partitioned by the vane portion 5a of the first vane 5 is the suction chamber 9 and the intermediate chamber 10. However, the rotation of the rotor shaft 4 proceeds and the vane portion 5a of the first vane 5 is advanced. The same applies to the case where the space partitioned by is the intermediate chamber 10 and the compression chamber 11. That is, 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 is true for the second vane 6.

  Further, as shown in FIG. 1, after 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 between the main bearing portion 2 c and the rotating shaft portion 4 b. The oil is returned to the oil sump 104 through the oil return hole 1 e provided in the outer peripheral portion of the cylinder 1. The refrigerating machine oil 25 supplied to the main bearing portion 3c is returned to the oil sump 104 through the gap between the main bearing portion 3c and the rotating shaft portion 4c. 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 is finally discharged together with the gas refrigerant into the space above the frame 2 from the discharge port 2d. After that, the oil is returned to the oil sump 104 through the oil return hole 1 e formed 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 into the space above the frame 2 from the oil drain hole 4 k above the rotor shaft 4. The oil is returned to the oil sump 104 through the oil return hole 1 e formed in the outer peripheral portion of the cylinder 1.

(Polishing of upper and lower end surfaces of vanes 5a and 6a)
As described above, the first vane 5 and the second vane 6 are members that partition the suction chamber 9, the intermediate chamber 10, and the compression chamber 11, which are three spaces formed in the through portion 1 f of the cylinder 1. In order to suppress the leakage of the gas refrigerant from these spaces, it is more effective that the gap between the vane portions 5a, 6a and the frame 2 and the gap between the vane portions 5a, 6a and the cylinder head 3 are smaller. Furthermore, in order to suppress the sliding loss between the vane portions 5a and 6a and the frame 2 and between the vane portions 5a and 6a and the cylinder head 3, the upper and lower end surfaces of the vane portions 5a and 6a are polished. Therefore, it is desirable that the ten-point average roughness is 0.8 [μm] or less.

  Hereinafter, planar polishing of the upper and lower end surfaces of the vane portions 5a and 6a will be described by taking as an example the case of processing the upper end surface of the vane portion 5a to which the vane aligner portion 5c of the first vane 5 is attached. In order to perform surface polishing in the range of the distance rv of the upper end surface of the vane portion 5a shown in FIG. 3, as shown in FIG. 3, the rotating grindstone does not interfere with the vane aligner portion 5c. As shown in FIG. Here, as a method of polishing the upper end surface of the vane portion 5a, for example, there is a method of using a tool called an end mill for cutting a workpiece while providing a large number of cutting edges on the end surface of a cylindrical body and rotating the cutting blade. It is possible to polish by bringing the end face of the end mill vertically into contact with the upper end of the vane 5a and reciprocating the upper end of the vane 5a in the direction of the distance rv shown in FIG. is there. Another method is a surface grinder, for example. The rotating grindstone is arranged so that its axis is parallel to the direction of the distance rv, the end surface of the rotating grindstone is brought into contact with the upper end of the vane portion 5a, and the rotating grindstone is rotated around the axis and at the same time in the direction of the distance rv. It is possible to polish by reciprocating. At this time, in order to polish the upper end surface of the vane portion 5a, it is desirable that the width in the same direction as the upper end surface of the vane portion 5a of the flat portion 5e is larger than the width of the upper end surface of the vane portion 5a. . In the present embodiment, since the flat portion 5e is formed on the vane aligner portion 5c, the rotating grindstone interferes with the vane aligner portion 5c when performing the planar polishing of the upper end surface of the vane portion 5a. Can be avoided. The same applies to the processing of the lower end surface of the vane portion 5a and the upper and lower end surfaces of the vane portion 6a. In addition, since the flat portions 5e and 6e are formed on the vane aligner portions 5c and 6c, the upper and lower end surfaces of the vane portions 5a and 6a are processed so that the ten-point average roughness is 0.8 [μm] or less. be able to. On the other hand, the ten-point average roughness when the upper and lower end surfaces of the vanes 5a and 6a are not polished is at least 3 [μm] or more. When the upper and lower end surfaces of the vane portions 5a and 6a are polished, the vane portions 5a and 6a and the frame 2 and between the vane portions 5a and 6a and the cylinder head 3 are compared with the case where the polishing is not performed. The mechanical loss on the sliding surface is suppressed by about 30%. Further, since the gap between the vane portions 5a, 6a and the frame 2 and the gap between the vane portions 5a, 6a and the cylinder head 3 can be reduced, high efficiency can be realized.

(Effect of Embodiment 1)
As described above, the flat surface processing of the upper and lower end surfaces of the vane portions 5a and 6a is performed by forming the flat surface portions 5e, 5f, 6e, and 6f on the vane aligner portions 5c, 5d, 6c, and 6d, respectively. In doing so, it is possible to avoid the rotating grindstone from interfering with the vane aligner portions 5c, 5d, 6c, and 6d, respectively.
In addition, this makes it possible to process the upper and lower end surfaces of the vane portions 5a and 6a to have a 10-point average roughness of 0.8 [μm] or less, between the vane portions 5a and 6a and the frame 2, and the vane. The sliding loss between the parts 5a, 6a and the cylinder head 3 can be suppressed, the gap between the vane parts 5a, 6a and the frame 2, and the gap between the vane parts 5a, 6a and the cylinder head 3 Since the seizure resistance and the wear resistance can be improved, high efficiency can be achieved.

  Further, by providing a predetermined appropriate gap δ between the vane tip portions 5b and 6b and the cylinder inner peripheral surface 1b so as to have the relationship of the above formula (1), the vane tip portions 5b and 6b are separated from the vane tip portions 5b and 6b. While suppressing the leakage of the refrigerant, it is possible to suppress a decrease in the compressor efficiency due to an increase in mechanical loss and to eliminate the wear of the vane tip portions 5b and 6b.

  In addition, vanes (first vane 5 and second vane 6) necessary for performing the compression operation so that the arc shapes of the vane tip portions 5b and 6b and the normal line of the cylinder inner peripheral surface 1b almost coincide with each other are provided in the cylinder. A mechanism that rotates around the center of the peripheral surface 1b as a rotation center can be realized by a configuration in which the rotor portion 4a and the rotating shaft portions 4b and 4c are integrated. For this reason, the rotation shaft portions 4b and 4c can be supported with a small diameter, so that the bearing sliding loss can be reduced, and the accuracy of the outer diameter and the rotation center of the rotor portion 4a can be improved. Leakage loss can be reduced by forming a narrow gap with 1b.

  In the present embodiment, the vanes installed on the rotor portion 4a of the rotor shaft 4 are the first vane 5 and the second vane 6. However, the present invention is not limited to this, and one or three vanes are not limited to this. It is good also as a structure by which the vane of a sheet or more is installed. For example, FIG. 8 is an exploded perspective view of the compression element 101 when three vanes are configured. In addition to the first vane 5 and the second vane 6, the third vane 70 is used as the third vane. It is installed. A bush 90 for sandwiching the vane portion of the third vane 70 is installed in the rotor portion 4a.

  Further, as shown in FIGS. 4, 5 and 7, the cross sections of the vane relief portions 4f and 4g are substantially circular, but the present invention is not limited to this, and the vane portions 5a and 6a are respectively vanes. As long as it does not contact the inner peripheral surfaces of the relief portions 4f and 4g, it may have an arbitrary shape (for example, a long hole shape or a rectangular shape).

  Further, as shown in FIG. 1, the frame 2 and the cylinder head 3 are configured such that the vane aligner bearing portions 2b and 3b which are the outer peripheral surfaces of the frame 2 and the cylinder head 3 are formed with concavities 2a and 3a which are concentric with the cylinder inner peripheral surface 1b. However, it is not limited to this. That is, the vane aligner bearing portions 2b and 3b may be of any shape as long as they are concentric with the cylinder inner peripheral surface 1b and the vane aligner portions 5c, 6c, 5d, and 6d can be fitted. It is good also as what forms by a ring-shaped groove | channel which can fit 5c, 6c, 5d, and 6d.

Further, as a material of the first vane 5 and the second vane 6, a sintered material impregnated with oil, cast iron, high-speed tool steel, or the like may be used in order to suppress seizure and wear. In order to suppress seizure and wear, as a fixed lubricating film, molybdenum disulfide, graphite, boron nitride, tungsten disulfide, talc, mica, manganese phosphate or soft metal plating as gold plating, silver plating, lead plating Or you may give copper plating etc. Further, as a method of increasing hardness for improving wear resistance, hard chrome plating, Ni—W plating, Fe—W plating, Co—W plating, Fe—C plating, Ni—Co plating, Cu—Sn plating or Surface treatment such as plating treatment such as Ni—Mo plating, ceramic coating treatment such as TiC, TiN, Al ₂ O ₃ , WC, etc., carburization treatment, nitriding treatment, or surface quenching by PVD method or CVD method may be performed. .

Embodiment 2. FIG.
The vane compressor 200 according to the present embodiment will be described focusing on differences from the vane compressor 200 according to the first embodiment.

(Formation of flat portions 5e, 5f, 6e, 6f for sliding in a fluid lubrication state)
The formation of the flat portions 5e, 5f, 6e, and 6f will be described below with the flat portion 5e of the vane aligner portion 5c as a representative. Since the wedge effect of the oil film decreases as the area of the flat surface portion 5e of the vane aligner portion 5c increases with respect to the area of the outer curved surface portion of the vane aligner portion 5c, the vane aligner portion 5c and the vane aligner bearing portion 2b It becomes impossible to slide in a lubricated state. Therefore, conditions for allowing the vane aligner portion 5c and the vane aligner bearing portion 2b to slide in the fluid lubrication state will be described below.

  FIG. 9 is a diagram showing a flow in a minute gap between two solid surfaces that move relative to each other in the second embodiment of the present invention, and FIG. 10 shows a vane aligner portion of the vane type compressor 200 according to the second embodiment. FIG. 11 is a schematic diagram showing the relationship between 5c and the vane aligner bearing portion 2b, and FIG. 11 is an analysis model in the second embodiment. The Reynolds fluid lubrication theory will be described below with reference to FIGS.

  FIG. 9 shows the flow in a minute gap between two solid surfaces that move relative to each other. When it is assumed that an incompressible fluid such as water or oil flows in a minute gap between two solid surfaces that move relative to each other, a partial differential equation relating to the pressure P generated in the fluid is expressed by the following equation (2): This equation (2) is called an incompressible Reynolds equation.

  Here, as shown in FIG. 9, x and y indicate coordinates parallel to the paper surface and perpendicular to each other. z represents a coordinate perpendicular to the paper surface and perpendicular to the x-axis and the y-axis. h is a gap between two solid surfaces and is a function of x. η is the viscosity coefficient of the refrigerator oil 25. u, v, and w represent fluid velocities in the x, y, and z axis directions, respectively. U1 represents the x-axis direction velocity of the lower surface in FIG. 9, U2 represents the x-axis direction velocity of the upper surface in FIG. 9, and V represents the y-axis direction velocity of the upper surface in FIG.

  Formula (2) is applied to the flow of the gap between the vane aligner portion 5c and the vane aligner bearing portion 2b. Originally, the vane aligner portion 5c has a shape as shown in FIG. 10, but in order to simplify the analysis model in the numerical analysis, as shown in FIG. 11, a virtual axis is provided in the vane aligner bearing portion 2b. Arranged. In FIG. 11, the fluid flowing in the gap between the vane aligner portion 5c and the virtual axis can be handled in the same manner as the flow between the two solid surfaces shown in FIG. Here, the x-axis in FIG. 9 is replaced with θ in FIG. θ is a positive angle counterclockwise from the maximum oil film thickness. The relationship between x and θ is expressed by the following formula (3).

  Here, Rc is the radius of the inner peripheral surface of the vane aligner bearing portion 2b. Then, when Expression (3) is substituted into Expression (2), the following Expression (4) is obtained.

  Originally, the vane aligner portion 5c rotates in the fixed vane aligner bearing portion 2b. However, in the analysis model, the vane aligner portion 5c is fixed and the vane aligner bearing portion is rotated. Here, the circumferential speeds U1 and U2 at arbitrary points A and B in FIG. 11 and the radial speed V at the point B are expressed by the following equations (5), (6) and (7), respectively. expressed.

  Here, ω is the angular velocity of the vane aligner bearing portion 2b, e is the distance from the center of the vane aligner bearing portion 2b to the center of the virtual axis, and φ is the center of the Y axis and the inner peripheral surface of the vane aligner bearing portion 2b. And the line connecting the center of the virtual axis. t represents time. Since the vane aligner portion 5c is fixed, the vane aligner portion 5c does not rotate. However, since the magnitude and direction of the load fluctuate, the vane aligner portion 5c moves in parallel in the vane aligner bearing portion 2b. The speed by this parallel movement is expressed as in the above equations (6) and (7). Each variable is made dimensionless as follows.

  Here, C is a radial gap between the vane aligner bearing portion 2b and the virtual shaft, L is a width of the vane aligner bearing portion 2b in the direction perpendicular to the paper surface, ε is an eccentricity of the virtual shaft with respect to the vane aligner bearing portion 2b, and A is a constant, the meaning of which will be described later. Then, when Expressions (5) to (12) are substituted into Expression (4), the following Expressions (13) and (14) are derived.

  Here, from C / Rc << 1, the formula (14) is expressed by the following formula (15).

  From the above equations (13) and (15), the following equation (16) is obtained.

  Here, the constant A is set as the following formula (17), and there is a relationship of formula (18).

  Further, the following equation (19) is derived from the equations (16) to (18).

  Then, the oil film pressure distribution in the plane of θ and z can be calculated by solving Equation (19) by the finite element method. However, the oil film pressure p in the portion corresponding to the flat portion 5e is analyzed as being “0”.

FIG. 12 is a diagram illustrating a state where the vane aligner portion 5c is fitted into the vane aligner bearing portion 2b in the vane type compressor 200 according to the second embodiment of the present invention.
Here, as shown in FIG. 12, the arc angle of the vane aligner portion 5c is α, the arc angle of the portion corresponding to the flat portion 5e of the vane aligner portion 5c is β, and in FIG. 12, the outside of the vane aligner portion 5c. Let γ be the arc angle of the portion corresponding to the intersection between the curved surface and the vane portion 5a.
The arc angle α can be set to 360 ° at the maximum when there is one vane, but is less than 180 ° at the maximum when there are two vanes, and 120 at the maximum when there are three vanes. Less than °. A particularly desirable angle is a maximum of 155 ° when two vanes are used, and a maximum of 95 ° when three vanes are used. This is because, for example, when there are two vanes, the length directions of the vane portions 5a and 6a do not match as shown in the “angle 45 °” and “angle 90 °” diagrams in FIG. This is because when the arc angle is 180 °, the vane aligner portions 5c and 6c interfere with each other.

  And in order to grasp | ascertain the lubrication characteristic of the vane aligner bearing part 2b and the vane aligner part 5c, when the eccentricity was 0.9, β / α was used as a parameter, and the oil film pressure was calculated analytically. The oil film pressure p is equal to the pressing surface pressure P acting on the vane aligner portion 5c described later. That is, an oil film pressure p sufficient to balance the pressing surface pressure P acting on the vane aligner bearing portion 2b is generated from the vane aligner portion 5c. Based on the pressing surface pressure P, the Sommerfeld number S shown in the following equation (20) corresponding to each β / α is calculated.

  In the above equation (20), η is the viscosity coefficient of the refrigerating machine oil 25, N is the rotational speed of the vane aligner portion 5c, P is the pressing surface pressure acting on the vane aligner portion 5c as described above, and Rc is the vane. This is the bearing radius of the aligner bearing portion 2b. By determining the Sommerfeld number S expressed by the equation (20), the lubrication characteristics of the vane aligner bearing portion 2b and the vane aligner portion 5c are uniquely determined.

FIG. 13 is an analysis result diagram showing the relationship between the Sommerfeld number S and β / α when the eccentricity ε = 0.9 in the vane compressor 200 according to the second embodiment of the present invention.
The graph shown in FIG. 13 is a graph showing the relationship between the Sommerfeld number S and β / α when the eccentricity ε = 0.9, and is expressed by the following equation (21).

  β / α = 0.1224ln (S) +0.2536 (21)

  If the condition is on the right side of the line in the graph of FIG. 13, the eccentricity ε is less than 0.9, and a stable fluid lubrication state can be ensured. That is, at least in the condition of β ≧ γ, if the following formula (22) is satisfied, the vane aligner portion 5c and the vane aligner bearing portion 2b can slide in the fluid lubrication state.

  β / α <0.1224ln (S) +0.2536 (22)

For example, when the Sommerfeld number S is 0.4, by setting β / α to 0.14 or less, the vane aligner portion 5c and the vane aligner bearing portion 2b can slide in a fluid lubrication state. It becomes.
Next, when the arc angle α = 150 and the arc angle β = 27.1, and β / α = 0.18, the case where the eccentricity ε is less than 0.9 and the case where it is 0.9 or more are compared. When the eccentricity ε is 0.9, the minimum oil film thickness is 0.9 μm. Generally, since the surface roughness of the vane aligner portion 5c and the vane aligner bearing portion 2b is about 1 μm, when the minimum oil film thickness is smaller than 1 μm, the vane aligner portion 5c and the vane aligner bearing portion 2 directly You will begin to touch. For this reason, a friction coefficient rises rapidly and the amount of wear increases. That is, when the eccentricity ε is 0.9 or more, the minimum oil film thickness becomes smaller than 1 μm and the wear amount increases. On the other hand, when the eccentricity ε is less than 0.9, direct contact between the vane aligner portion 5c and the vane aligner bearing portion 2b is suppressed, and sliding in a fluid lubrication state is possible.

In addition, although the above content was demonstrated in the relationship between the vane aligner part 5c and the vane aligner bearing part 2b, the relationship between the vane aligner part 6c and the vane aligner bearing part 2b, the vane aligner part 5d, and the vane aligner bearing part 3b This also applies to the relationship between the vane aligner portion 6d and the vane aligner bearing portion 3b.
Although the above description has been given for the case where there are two vanes, if the formula (22) holds even if there are three or four vanes, the vane aligner portion 5c and the vane aligner bearing portion 2b slide in a fluid lubricated state. It is possible to move.

(Effect of Embodiment 2)
According to the above conditions, the plane portions 5e, 5f, 6e, and 6f are formed in the vane aligner portions 5c, 5d, 6c, and 6d, respectively. The sliding between the portions 5c and 6c and the vane aligner bearing portion 2b and the sliding between the vane aligner portion 5d and the vane aligner portion 6d and the vane aligner bearing portion 3b can be maintained in a fluid lubrication state at all times. Improves attachment and wear resistance, and at the same time achieves higher efficiency.

  1 cylinder, 1a suction port, 1b cylinder inner peripheral surface, 1c notch, 1d discharge port, 1e oil return hole, 1f penetration, 2 frame, 2a recess, 2b vane aligner bearing, 2c main bearing, 2d discharge Port, 2f, 2g stopper, 3 cylinder head, 3a recess, 3b vane aligner bearing, 3c main bearing, 3f, 3g stopper, 4 rotor shaft, 4a rotor, 4b, 4c rotating shaft, 4d, 4e Part, 4f, 4g vane relief part, 4h-4j oil supply passage, 4k oil drain hole, 5 first vane, 5a vane part, 5b vane tip part, 5c, 5d vane aligner part, 5e, 5f flat part, 6 second Vane, 6a Vane part, 6b Vane tip, 6c, 6d Vane aligner part, 6e, 6 Flat portion, 7 bush, 7a bush center, 8 bush, 8a bush center, 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, 70 3rd vane, 90 Bush, 101 Compression element, 102 Electric element, 103 Airtight container, 104 Oil sump, 200 Vane compressor

Claims (7)

A cylinder having a cylindrical inner peripheral surface;
A rotor having a cylindrical rotor portion that rotates around a rotation axis that is shifted from the central axis of the inner peripheral surface by a predetermined distance inside the cylinder, and a rotation shaft portion that transmits a rotational force to the rotor portion. A shaft,
A frame that closes one opening of the inner peripheral surface of the cylinder and supports the rotating shaft by a main bearing;
A cylinder head that closes the other opening of the inner peripheral surface of the cylinder and supports the rotating shaft by a main bearing portion;
At least one vane provided in the rotor portion and formed in an arc shape in which a tip portion protruding from the rotor portion is convex outward;
In a vane compressor equipped with
The inner surface of the vane, the outer peripheral portion of the rotor portion, and the inner periphery of the cylinder are in a state where the normal line of the arc shape of the tip end portion of the vane and the normal line of the inner peripheral surface of the cylinder always coincide with each other. The vane is supported so as to compress the refrigerant in a space surrounded by a peripheral surface, the vane is supported so as to be rotatable and movable with respect to the rotor portion, and the tip end portion of the vane is the inner periphery of the cylinder. Vane support means for holding the tip portion and the inner peripheral surface so as to have a predetermined gap when moved to the maximum surface side,
The rotor shaft is configured by integrally forming the rotor portion and the rotating shaft portion,
The radius of curvature of the arc shape of the tip of the vane is substantially the same as the radius of curvature of the inner peripheral surface of the cylinder,
The vane support means includes
A bush holding portion penetrating in the central axis direction so that a cross section perpendicular to the central axis direction of the rotor portion is substantially circular, in the vicinity of the outer peripheral portion of the rotor portion;
A pair of substantially semi-cylindrical objects inserted into the bush holding portion, and a bush for sandwiching the vane in the bush holding portion;
In the vane, an end surface on the inner peripheral surface side that is the center of the inner peripheral surface of the cylinder is formed so as to penetrate the rotor portion in the central axis direction of the rotor portion so as not to contact the rotor portion. The vane relief part,
Composed by
The vane has a pair of arcuate vane aligner portions provided near the end surface on the frame side and the center side of the rotor portion, and near the end surface on the cylinder head side and the center side of the rotor portion,
Concave portions or groove portions concentric with the inner peripheral surface of the cylinder are formed on the cylinder and the cylinder side end surface of the cylinder head,
The vane aligner portion is fitted into the recess or the groove portion, and is supported by a vane aligner bearing portion that is an outer peripheral surface of the recess or the groove portion. A vane type compressor characterized in that a flat portion perpendicular to the surface is formed. In the arc shape of the vane aligner portion, the arc angle of the portion corresponding to the flat portion formed in the vane aligner portion is β, and the vane tip portion side surface of the vane aligner portion and the vane aligner portion 2. The vane according to claim 1, wherein the flat surface portion is formed so as to satisfy β ≧ γ, where γ is an arc angle of a portion corresponding to a portion where the end surface of the vane provided with is γ. Mold compressor. When the arc angle of the arc shape of the vane aligner portion is α and the Sommerfeld number is S, the plane portion is formed so as to satisfy β / α <0.1224ln (S) +0.2536. The vane type compressor according to claim 2, 4. The vane according to claim 1, wherein a ten-point average roughness of an end face of the vane facing the frame and the cylinder head is 0.8 [μm] or less. 5. Mold compressor. 5. The vane mold according to claim 1, wherein either one of an upper end and a lower end of the vane is polished after the planar portion is formed on the vane aligner portion. Compressor. 6. The vane compressor according to claim 5, wherein either one of an upper end and a lower end of the vane is polished by an end mill. 6. The vane compressor according to claim 5, wherein either one of the upper end and the lower end of the vane is polished by a surface grinder.

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