JP5595600B2 - 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).

  Further, the inside 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 semicircular rods is formed near the outer periphery of the rotor portion. There has also been proposed a vane type compressor in which a vane is held so as to be rotatable (swingable) with respect to a rotor portion via a clamping member (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), the direction of the vane is regulated by a vane groove formed in the rotor portion of the rotor shaft. That is, the vane is held so as to always have the same inclination with respect to the rotor portion. 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. Therefore, in the conventional vane type compressor, a contrivance has been made to reduce the pressing force of the vane against the cylinder inner peripheral surface as much as possible.

  The conventional vane type compressor described in Patent Document 2 is also one of those proposed to solve the above-described problems. 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 For this reason, it is possible to configure the radius of the cylinder inner peripheral surface and the radius of the vane tip arc to be substantially equal so that the vane front end extends along the cylinder inner peripheral surface. Therefore, the vane tip and the cylinder inner peripheral surface can be configured in a non-contact manner. Alternatively, even when the vane tip and the cylinder inner peripheral surface come into contact with each other, the lubrication state between them can be made into a fluid lubrication state with a sufficient oil film. As a result, it is possible to improve the sliding state of the vane tip, which is a problem of the conventional vane compressor.

  However, since the conventional vane type compressor described in Patent Document 2 requires that the interior of the rotor shaft 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.

The present invention has been made to solve the above-described problems, and an object thereof is to provide a vane type compressor shown below.
(1) First, it is possible to realize a mechanism in which a vane rotates around the center of a cylinder while reducing bearing sliding loss and suppressing deterioration of the outer diameter of the rotor portion and the accuracy of the rotation center. The object is to obtain a vane compressor.
(2) Secondly, an object of the present invention is to obtain a vane type compressor capable of realizing the purpose of the above (1) while the vane tip and the cylinder inner peripheral surface can be configured in a non-contact manner.
(3) Thirdly, an object of the present invention is to provide a vane type compressor in which the vane and the cylinder inner peripheral surface can slide in a fluid lubrication state while realizing the object of the above (1) or (2). .

The vane type compressor according to the present invention includes a cylinder having a cylindrical through hole, a frame that closes one open end of the through hole of the cylinder, and a cylinder that closes the other open end of the through hole of the cylinder. A rotor having a head, a cylindrical rotor portion that rotates about a rotation axis that is shifted from the central axis of the through hole by a predetermined distance inside the cylinder, and a shaft portion that transmits a rotational force to the rotor portion, and the rotor In the vane type compressor having a plurality of vanes formed in a circular arc shape that is provided in the portion and the tip portion protruding from the rotor portion is convex outward,
The vane is supported by the rotor portion so as to be swingable and movable in a substantially centrifugal direction, and a first concave portion or a first convex portion is formed on a surface facing the vane frame, and the vane cylinder head and The second concave portion or the second convex portion is formed on the opposite surface of the first convex portion, and the third convex portion or the first convex portion of the corresponding vane inserted into the first concave portion of the corresponding vane is inserted. A plurality of first vane aligners provided on the frame, such that the third concave portion is formed, and the third convex portion or the third concave portion is rotatable about the central axis of the through hole of the cylinder. A fourth convex portion inserted into the second concave portion of the corresponding vane or a fourth concave portion into which the second convex portion of the corresponding vane is inserted is formed, and the fourth convex portion or the fourth concave portion is formed. To the cylinder head so that it can rotate around the center axis of the through-hole of the cylinder. A plurality of second vane aligners, and each of the plurality of first vane aligners has a third convex portion or a first convex portion inserted into the third concave portion of each other. Each of the plurality of second vane aligners is provided in the frame so as to be rotatable without interfering, and each of the plurality of second vane aligners is inserted into the fourth convex portion or the fourth concave portion of each other. Is provided in the cylinder head so as to be rotatable without interference.

  The vane type compressor according to the present invention can realize a mechanism in which the vane rotates around the center of the cylinder with a configuration in which the rotor portion and the rotation shaft are integrated. For this reason, a bearing sliding loss can be reduced because a rotating shaft can be supported by a small diameter support structure. In addition, the accuracy of the outer diameter of the rotor portion and the rotation center can be improved. Therefore, the vane type compressor according to the present invention can reduce leakage loss by forming a narrow gap between the rotor portion and the inner circumferential surface of the cylinder.

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 which concerns on Embodiment 1 of this invention. It is the top view or bottom view which shows the vane aligner of the compression element which concerns on Embodiment 1 of this invention. It is a plane sectional view of the compression element concerning Embodiment 1 of the present invention. It is explanatory drawing (planar sectional drawing) which shows the compression operation | movement of the compression element which concerns on Embodiment 1 of this invention. It is a principal part enlarged view (bottom surface sectional view) which shows the vane vicinity of the compression element which concerns on Embodiment 2 of this invention. It is a perspective view which shows the vane and vane aligner of the compressor which concerns on Embodiment 3 of this invention. It is the top view or bottom view which shows the vane aligner of the compression element which concerns on Embodiment 4 of this invention. It is a perspective view which shows the vane of the compression element which concerns on Embodiment 4 of this invention. It is a side view which shows the connection method of the vane which concerns on Embodiment 4 of this invention, and a vane aligner. It is a longitudinal cross-sectional view which shows the vane type compressor which concerns on Embodiment 5 of this invention. It is a top view or a bottom view showing a vane aligner provided in a compression element of a vane type compressor concerning Embodiment 5 of the present invention.

  Hereinafter, in each of the following embodiments, an example of a vane compressor according to the present invention will be described. In the following embodiments, a hermetic vane compressor will be described. However, the vane compressor according to the present invention is not limited to a hermetic vane compressor. The characteristic part of the vane type compressor according to the present invention is a compression element, and various vane type compressors such as a vane type compressor driven by an engine and a vane type compressor housed in an open container, etc. The present invention can be implemented.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing a vane type compressor according to Embodiment 1 of the present invention.
In a vane type compressor 200 (sealed type) shown in FIG. 1, a compression element 101 and an electric element 102 that drives the compression element 101 are housed in a sealed container 103. The compression element 101 is disposed at the lower part of the sealed container 103. Refrigerating machine oil 25 stored at the bottom of the sealed container 103 is guided to the compression element 101 by an oil supply mechanism (not shown). Thereby, each sliding part of the compression element 101 is lubricated. The electric element 102 is disposed on the upper portion of the sealed container 103 (more specifically, above the compression element 101).

  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. 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 portion 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. In addition, although the vane type compressor 200 (sealed type) according to Embodiment 1 shows a high pressure type in which the inside of the sealed container 103 becomes high pressure, a low pressure type in which the inside of the sealed container 103 becomes low pressure is also shown. Of course. Further, the vane type compressor 200 according to the first embodiment shows a case where the number of vanes is two (vanes 9 and 10 in FIG. 1).

(Detailed structure of compression element 101)
FIG. 2 is an exploded perspective view showing the compression element according to Embodiment 1 of the present invention. FIG. 3 is a plan view or bottom view showing the vane aligner of the compression element. 3A shows a bottom view of the vane aligner 5 and a plan view of the vane aligner 6, and FIG. 3B shows a bottom view of the vane aligner 7 and a plan view of the vane aligner 8. 3A is the inner peripheral shape of the vane aligners 7 and 8, and the two-dot chain line shown in FIG. 3B is the inner peripheral shape of the vane aligners 5 and 6.
Hereinafter, the detailed structure of the compression element 101 which is a characteristic part of the vane type compressor 200 according to the first embodiment will be described with reference to FIGS. 2, 3 and 1.

As shown in FIG. 2, the compression element 101 has the following elements.
(1) Cylinder 1: The overall shape is substantially cylindrical, and both ends in the central axis direction are open. A suction port 1a is opened from the outer peripheral surface to the inner peripheral surface 1b. In addition, the outer peripheral part shape of the cylinder 1 is arbitrary and may be appropriately determined according to the shape of the container in which the cylinder 1 is stored. That is, the cylinder 1 should just have the cylindrical through-hole formed in the center part. In the vane type compressor 200 according to the first embodiment, the cylinder 1 is housed in a substantially cylindrical airtight container 103 whose both ends are closed, so that the overall shape of the cylinder 1 is formed in a substantially cylindrical shape.

(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. A ring groove-shaped vane aligner holding portion 2a (shown in FIG. 1) that is concentric with the inner peripheral surface 1b of the cylinder 1 is formed on the cylinder 1 side end surface (the lower surface in FIG. 2) of the substantially disk-shaped member. Yes. A ring-shaped vane aligner 5 and a vane aligner 7 to be described later are inserted into the vane aligner holding portion 2a in an overlapping manner. 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 bearing portion 2b (shown in FIG. 1). The bearing part 2b supports the rotating shaft part 4b of the rotor shaft 4 mentioned later rotatably. Further, a discharge port 2 c is formed at a substantially central portion of the frame 2. The discharge port 2c may be formed in a cylinder head 3 to be described later.

(3) Cylinder head 3: A cylindrical member is provided at a lower portion of a substantially disk-shaped member, and a longitudinal section thereof is substantially T-shaped (see FIG. 1). The substantially disk-shaped member closes the other opening (lower side in FIG. 2) of the cylinder 1. A ring groove-shaped vane aligner holding portion 3 a concentric with the inner peripheral surface 1 b of the cylinder 1 is formed on the cylinder 1 side end surface (the upper surface in FIG. 2) of the substantially disk-shaped member. A ring-shaped vane aligner 6 and a vane aligner 8 to be described later are inserted into the vane aligner holding portion 3a in an overlapping manner. 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. The through hole is provided with a bearing portion 3b (shown in FIG. 1). The bearing part 3b supports the rotating shaft part 4c of the rotor shaft 4 mentioned later rotatably.

(4) Rotor shaft 4: A substantially cylindrical rotor portion 4a, a rotary shaft portion 4b provided on the upper portion of the rotor portion 4a so as to be concentric with the rotor portion 4a, and a rotor so as to be concentric with the rotor portion 4a. The rotating shaft part 4c provided in the lower part of the part 4a is provided. The rotor portion 4a performs a rotational motion around a rotational axis that is eccentric by a predetermined distance from the central axis of the cylinder 1. As described above, the rotary shaft portion 4b and the rotary shaft portion 4c are rotatably supported by the bearing portion 2b and the bearing portion 3b. 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 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. 4 described later). .

(5) Vane aligner 5: It is provided with a ring-shaped member and a vane holding portion 5a erected on one end surface (lower side in FIG. 2) in the central axis direction of the ring-shaped member. The vane holding part 5a is, for example, a plate-like protrusion having a substantially square cross section. In the first embodiment, the vane holding portion 5a is formed in the normal direction of the ring-shaped member. Further, the distance between the outermost peripheral portion of the vane holding portion 5a and the ring-shaped member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) is slightly smaller than the radius of the inner peripheral portion of the vane aligner 7 described later. (See FIG. 3). Here, the vane aligner 5 corresponds to the first vane aligner in the present invention, and the vane holding portion 5a corresponds to the third convex portion in the present invention.

(6) Vane aligner 6: A ring-shaped member and a vane holding portion 6a provided upright on one end surface (upper side in FIG. 2) in the central axis direction of the ring-shaped member. The vane holding part 6a is, for example, a plate-like protrusion having a substantially square cross section. In the first embodiment, the vane holding portion 6a is formed in the normal direction of the ring-shaped member. Further, the distance between the outermost peripheral portion of the vane holding portion 6a and the ring-shaped member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) is slightly smaller than the radius of the inner peripheral portion of the vane aligner 8 described later. (See FIG. 3). Here, the vane aligner 6 corresponds to the second vane aligner in the present invention, and the vane holding portion 6a corresponds to the fourth convex portion in the present invention.

(7) Vane aligner 7: It is provided with a ring-shaped member and a vane holding portion 7a erected on one end surface (lower side in FIG. 2) in the central axis direction of the ring-shaped member. The vane holding part 7a is, for example, a plate-like protrusion having a substantially square cross section. In the first embodiment, the vane holding portion 7a is formed in the normal direction of the ring-shaped member. Further, the ring-shaped member of the vane aligner 7 has a diameter of the outer peripheral portion thereof substantially equal to the diameter of the outer peripheral portion of the ring-shaped member of the vane aligner 5. Here, like the vane aligner 5, the vane aligner 7 corresponds to the first vane aligner in the present invention, and the vane holding portion 7a corresponds to the third convex portion in the present invention.

(8) Vane aligner 8: A ring-shaped member and a vane holding portion 8a provided upright on one end surface (upper side in FIG. 2) in the central axis direction of the ring-shaped member. The vane holding portion 8a is, for example, a plate-like protrusion having a substantially square cross section. In the first embodiment, the vane holding portion 8a is formed in the normal direction of the ring-shaped member. Further, the ring-shaped member of the vane aligner 8 has a diameter of the outer peripheral portion thereof substantially equal to the diameter of the outer peripheral portion of the ring-shaped member of the vane aligner 6. Here, like the vane aligner 6, the vane aligner 8 corresponds to the second vane aligner in the present invention, and the vane holding portion 8a corresponds to the fourth convex portion in the present invention.

(9) Vane 9: A plate-like member having a substantially square shape when viewed from the side. A front end portion 9a (a front end portion protruding from the rotor portion 4a) located on the inner peripheral surface 1b side of the cylinder 1 is formed in an arc shape that protrudes outward in plan view. The arcuate radius of the tip 9a is substantially the same as the radius of the inner peripheral surface 1b of the cylinder 1. A vane holding portion 5a of the vane aligner 5 is inserted on the upper surface (a surface facing the frame 2) in the vicinity of an end portion (hereinafter referred to as an inner peripheral end portion) opposite to the tip end portion 9a of the vane 9. A slit-shaped rear groove 9b is formed. Similarly, a slit-like back groove 9b into which the vane holding portion 6a of the vane aligner 6 is inserted is formed on the lower surface (the surface facing the cylinder head 3) in the vicinity of the inner peripheral end of the vane 9. . In the first embodiment, the back groove 9b is formed from the inner peripheral end along the longitudinal direction of the vane 9 up to a range where the vane holding part 5a and the vane holding part 6a are inserted. Of course, these back surface grooves 9 b may be formed in the entire area of the upper surface and the lower surface of the vane 9 along the longitudinal direction of the vane 9. Here, the back surface groove 9b into which the vane holding portion 5a is inserted corresponds to the first recess in the present invention. Moreover, the back surface groove | channel 9b in which the vane holding | maintenance part 6a is inserted corresponds to the 2nd recessed part in this invention.

(10) Vane 10: A plate-like member having a substantially square shape when viewed from the side. A tip portion 10a (tip portion protruding from the rotor portion 4a) located on the inner peripheral surface 1b side of the cylinder 1 is formed in an arc shape that protrudes outward in plan view. The arcuate radius of the tip portion 10a is configured to be substantially equal to the radius of the inner peripheral surface 1b of the cylinder 1. In addition, a vane holding portion 7a of the vane aligner 7 is inserted in an upper surface (a surface facing the frame 2) in the vicinity of an end portion (hereinafter referred to as an inner peripheral end portion) opposite to the tip portion 10a of the vane 10. A slit-shaped rear groove 10b is formed. Similarly, a slit-like back surface groove 10b into which the vane holding portion 8a of the vane aligner 8 is inserted is formed on the lower surface (the surface facing the cylinder head 3) in the vicinity of the inner peripheral end of the vane 10. . In the first embodiment, the back groove 10b is formed along the longitudinal direction of the vane 10 from the inner peripheral side end portion to a range where the vane holding portion 7a and the vane holding portion 8a are inserted. Of course, these back surface grooves 10 b may be formed in the entire area of the upper surface and the lower surface of the vane 10 along the longitudinal direction of the vane 10. Here, the back surface groove 10b into which the vane holding portion 7a is inserted corresponds to the first recess in the present invention. Moreover, the back surface groove | channel 10b in which the vane holding | maintenance part 8a is inserted corresponds to the 2nd recessed part in this invention.

(11) Bushes 11, 12: A substantially semi-cylindrical member is configured as a pair. The bush 11 is rotatably inserted into the bush holding portion 4d of the rotor portion 4a while sandwiching the vane 9. The bush 12 is rotatably inserted into the bush holding portion 4e of the rotor portion 4a in a state where the vane 10 is sandwiched. That is, when the vane 9 slides between the bushes 11, the vane 9 can move in a substantially centrifugal direction with respect to the rotor portion 4a (a centrifugal direction with respect to the center of the inner peripheral surface 1b of the cylinder 1). . Further, the vane 9 can be swung by the rotation of the bush 11 within the bush holding portion 4d of the rotor portion 4a. Similarly, when the vane 10 slides between the bushes 12, the vane 10 can move in a substantially centrifugal direction with respect to the rotor portion 4a. Further, the vane 10 can be swung as the bush 12 rotates within the bush holding portion 4e of the rotor portion 4a.

  The vane holders 5a and 6a of the vane aligners 5 and 6 are inserted into the back groove 9b of the vane 9, and the vane holders 7a and 8a of the vane aligners 7 and 8 are inserted into the back groove 10b of the vane 10. The direction is regulated so that the normal line of the arcs at the tips of the vanes 9 and 10 always coincides with the normal line of the cylinder inner peripheral surface 1b.

(Description of operation)
Next, the operation of the vane compressor 200 according to the first embodiment will be described.
When the rotational shaft portion 4b of the rotor shaft 4 receives rotational power from the electric element 102 (engine in the case of engine driving) as a drive 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). And a pair of bushes 11 and 12 currently hold | maintained in the bush holding | maintenance parts 4d and 4e, and the vanes 9 and 10 hold | maintained rotatably between the pair of bushes 11 and 12 also rotate with the rotor part 4a. .

  At this time, the vane aligner 5 in which the vane holding portion 5a is slidably inserted into the back surface groove 9b of the vane 9 also rotates in the vane aligner holding portion 2a. Further, the vane aligner 6 in which the vane holding portion 6a is slidably inserted into the back surface groove 9b of the vane 9 also rotates in the vane aligner holding portion 3a. As described above, the vane aligner holding portion 2 a into which the vane aligner 5 is inserted and the vane aligner holding portion 3 a into which the vane aligner 6 is inserted are formed concentrically with the inner peripheral surface 1 b of the cylinder 1. For this reason, since the vane holding part 5a and the vane holding part 6a rotate about the central axis of the inner peripheral surface 1b of the cylinder 1, the longitudinal direction of the vane 9 is the method of the inner peripheral surface 1b of the cylinder 1. The direction is regulated so as to be in the line direction.

  Similarly, the vane aligner 7 in which the vane holding portion 7a is slidably inserted into the back surface groove 10b of the vane 10 also rotates within the vane aligner holding portion 2a. Further, the vane aligner 8 in which the vane holding portion 8a is slidably inserted into the back surface groove 10b of the vane 10 also rotates in the vane aligner holding portion 3a. As described above, the vane aligner holding portion 2 a into which the vane aligner 7 is inserted and the vane aligner holding portion 3 a into which the vane aligner 8 is inserted are formed concentrically with the inner peripheral surface 1 b of the cylinder 1. For this reason, since the vane holding part 7a and the vane holding part 8a rotate around the central axis of the inner peripheral surface 1b of the cylinder 1, the longitudinal direction of the vane 10 is the method of the inner peripheral surface 1b of the cylinder 1. The direction is regulated so as to be in the line direction.

  Further, the vane 9 and the vane 10 are pressed in the direction of the inner peripheral surface 1 b of the cylinder 1 by centrifugal force or the like, and the tip end portion 9 a of the vane 9 and the tip end portion 10 a of the vane 10 are along the inner peripheral surface 1 b of the cylinder 1. Slide. At this time, the radius of the arc of the tip portion 9a of the vane 9 and the radius of the arc of the tip portion 10a of the vane 10 are substantially the same as the radius of the inner peripheral surface 1b of the cylinder 1, and the normal line between them is almost the same. Therefore, a sufficient oil film is formed between the two to provide fluid lubrication. As a configuration for moving the vane 9 in the direction of the inner peripheral surface 1b of the cylinder 1, for example, a high-pressure or intermediate-pressure refrigerant is introduced into the space near the inner peripheral end of the vane 9, and the tip of the vane 9 is moved. It is good also as a structure using the pressure difference of the pressure of the part 9a side, and the pressure of the inner peripheral side edge part side. Further, for example, the vane 9 may be pushed by an elastic member such as a spring to move the vane 9 toward the inner peripheral surface 1 b of the cylinder 1. The configuration when moving the vane 10 toward the inner peripheral surface 1b of the cylinder 1 is also the same.

As the constituent members of the compression element 101 operate as described above, the refrigerant is compressed in the compression element 101 as follows.
FIG. 4 is a plan sectional view of the compression element according to Embodiment 1 of the present invention. This figure shows a state where the rotation angle of the rotor portion 4a (rotor shaft 4) is 90 ° as will be described later with reference to FIG. Hereinafter, based on FIG. 4, the refrigerant | coolant compression operation | movement of the compression element 101 which concerns on this Embodiment 1 is demonstrated.

  As shown in FIG. 4, the rotor portion 4 a of the rotor shaft 4 and the inner peripheral surface 1 b of the cylinder 1 are in closest contact at one place (the closest contact shown in FIG. 4). Further, the vane 9 and the inner peripheral surface 1b of the cylinder 1 and the vane 10 and the inner peripheral surface 1b of the cylinder 1 slide at one place, respectively, so that three spaces (suction chamber 13, intermediate chamber) are formed in the cylinder 1. 14, compression chamber 15) is formed. In the suction chamber 13, a suction port 1 a communicating with the low pressure side of the refrigeration cycle is opened. The compression chamber 15 communicates with the discharge port 2 c formed in the frame 2. The discharge port 2c is closed with a discharge valve (not shown) except during discharge. The intermediate chamber 14 communicates with the suction port 1a up to a certain rotational angle range of the rotor portion 4a, but thereafter has a rotational angle range that does not communicate with either the suction port 1a or the discharge port 2c, and thereafter the discharge port 2c. Communicate with.

  FIG. 5 is an explanatory view (plan sectional view) showing the compression operation of the compression element according to Embodiment 1 of the present invention. Hereinafter, the manner in which the volumes of the suction chamber 13, the intermediate chamber 14, and the compression chamber 15 change with the rotation of the rotor portion 4a (rotor shaft 4) will be described with reference to FIG. In describing the volume change of each space (suction chamber 13, intermediate chamber 14, compression chamber 15), the rotation angle of the rotor portion 4a (rotor shaft 4) is defined as follows. First, the sliding part (contact part) between the vane 9 and the inner peripheral surface 1b of the cylinder 1 coincides with the closest point (the part where the rotor part 4a of the rotor shaft 4 and the inner peripheral surface 1b of the cylinder 1 are in closest contact). This state is defined as “angle 0 °”. In FIG. 5, in the state of “angle 0 °”, “angle 45 °”, “angle 90 °”, and “angle 135 °”, the positions of the vanes 9 and 10 and the suction chamber 13 and the intermediate chamber 14 at that time are shown. And the state of the compression chamber 15 is shown.

  Note that the rotation of the rotor portion 4a (rotor shaft 4) in FIG. 5 is the same as the rotation direction (clockwise direction) shown in FIG. Further, in FIG. 5, the state after “angle 180 °” is not shown. When “angle 180 °” is reached, the state is the same as the state in which the vane 9 and the vane 10 are switched at “angle 0 °”. This is because the same compression operation is performed from “angle 0 °” to “angle 135 °”.

  Further, the suction port 1a is located between the closest point and a point A (see FIG. 4) where the tip 9a of the vane 9 and the inner peripheral surface 1b of the cylinder 1 slide in the state of “angle 90 °” (for example, , Approximately 45 °). That is, the suction port 1a opens in the range from the closest point to the point A. However, in FIGS. 4 and 5, the suction port 1 a is simply expressed as “suction”.

  In addition, the discharge port 2c is provided in the vicinity of the closest contact and on the upstream side in the rotation direction of the rotor portion 4a (left side in FIGS. 4 and 5) by a predetermined angle (distance) from the closest contact (for example, the closest contact). About 30 ° from the upstream side in the rotational direction of the rotor portion 4a). However, in FIGS. 4 and 5, the discharge port 2 c is simply expressed as “discharge”.

  At “angle 0 °” in FIG. 5, the space on the right side partitioned by the closest contact and the vane 10 communicates with the suction port 1 a in the intermediate chamber 14 and sucks gas (refrigerant). The space on the left side that is partitioned by the closest contact and the vane 10 becomes a compression chamber 15 that communicates with the discharge port 2c.

  At “angle 45 °” in FIG. 5, the space partitioned by the vane 9 at the closest point becomes the suction chamber 13, and the space partitioned by the vane 9 and the vane 10 becomes the intermediate chamber 14. The suction chamber 13 and the intermediate chamber 14 communicate with the suction port 1a. Since the volume of the intermediate chamber 14 becomes larger than that at the “angle 0 °”, the gas suction is continued. The space partitioned by the vane 10 and the closest contact is the compression chamber 15, and the volume of the compression chamber 15 becomes smaller than that at the “angle 0 °”, and the refrigerant is compressed and its pressure gradually increases.

  At “angle 90 °” in FIG. 5, the tip 9 a of the vane 9 overlaps with the point A on the inner peripheral surface 1 b of the cylinder 1, so that the intermediate chamber 14 does not communicate with the suction port 1 a. Thereby, the suction of the gas in the intermediate chamber 14 is completed. In this state, the volume of the intermediate chamber 14 is substantially maximum. The volume of the compression chamber 15 becomes even smaller than when the angle is 45 °, and the refrigerant pressure rises. The volume of the suction chamber 13 becomes larger than that at the “angle 45 °”, and the suction is continued.

  At “angle 135 °” in FIG. 5, the volume of the intermediate chamber 14 becomes smaller than that at “angle 90 °”, and the refrigerant pressure rises. Further, the volume of the compression chamber 15 becomes smaller than that at the “angle 90 °”, and the pressure of the refrigerant rises. The volume of the suction chamber 13 becomes larger than that at the “angle 90 °”, and the suction is continued.

  Thereafter, the vane 10 approaches the discharge port 2c, but when the pressure in the compression chamber 15 exceeds the high pressure of the refrigeration cycle (including the pressure necessary to open a discharge valve not shown), the discharge valve opens and the refrigerant in the compression chamber 15 Is discharged into the sealed container 103.

  When the vane 10 passes through the discharge port 2c, a little high-pressure refrigerant remains (loss) in the compression chamber 15. When the compression chamber 15 disappears at an “angle of 180 °” (not shown), the high-pressure refrigerant changes into a low-pressure refrigerant in the suction chamber 13. At “angle 180 °”, the suction chamber 13 moves to the intermediate chamber 14, the intermediate chamber 14 moves to the compression chamber 15, and the compression operation is repeated thereafter.

  In this way, the volume of the suction chamber 13 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 14, but the volume gradually increases to the middle, and further the gas suction is continued. On the way, the volume of the intermediate chamber 14 becomes the maximum and the communication with the suction port 1a is lost, so the gas suction is terminated here. Thereafter, the volume of the intermediate chamber 14 gradually decreases and compresses the gas. Thereafter, the intermediate chamber 14 moves to the compression chamber 15 and continues to compress the gas. The gas compressed to a predetermined pressure is discharged from a discharge port (for example, discharge port 2c) formed in a portion of the cylinder 1 or the frame 2 or the cylinder head 3 that opens to the compression chamber 15.

  As described above, in the vane type compressor 200 according to the first embodiment, the compression operation can be performed so that the arcs of the vane tip portions 9a and 10a and the normal line of the inner peripheral surface 1b of the cylinder 1 always coincide with each other. . In addition, a mechanism in which the vane 9 and the vane 10 necessary for performing such a compression operation rotate around the center of the cylinder 1 is realized by integrally configuring the rotary shaft portions 4b and 4c and the rotor portion 4a. (That is, it is realized without using end plates provided at both ends of the rotor portion of the conventional vane type compressor). For this reason, the vane type compressor 200 according to the first embodiment reduces the bearing sliding loss by being able to support the rotating shaft portions 4b and 4c with the small-diameter bearing portions 2b and 3b, and the outside of the rotor portion 4a. The accuracy of the 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.

  Further, the vane type compressor 200 according to the first embodiment substantially matches the radius of the arc of the tip 9a of the vane 9 and the tip 10a of the vane 10 with the radius of the inner peripheral surface 1b of the cylinder 1, The normals are configured to substantially match. For this reason, the sliding part of vane tip part 9a, 10a becomes fluid lubrication, and the sliding resistance of vane tip part 9a, 10a can be reduced significantly. For this reason, the sliding loss of the vane compressor 200 can be significantly reduced, and the wear of the tip 9a of the vane 9, the tip 10a of the vane 10, and the inner peripheral surface 1b of the cylinder 1 can be suppressed. Can do.

  In the first embodiment, the vane aligner holding portion 2a formed on the frame 2 and the vane aligner holding portion 3a formed on the cylinder head 3 have a ring groove shape, but the vane aligner holding portion 2a and the vane aligner holding are also provided. The shape of the part 3a is not limited to this. That is, in the vane aligner holding part 2a, the sliding part with the vane aligners 5 and 7 is a cylindrical surface on the outer peripheral side. For this reason, the shape of the vane aligner holding portion 2a may be a recess whose outer diameter is substantially equal to the outer diameter of the vane aligners 5 and 7 (that is, a shape obtained by removing the protrusion on the center side of the ring groove). Similarly, the shape of the vane aligner holding portion 3a may be a recess whose outer diameter is substantially the same as the outer diameter of the vane aligners 6 and 8 (that is, a shape obtained by removing the protrusion on the center side of the ring groove).

  Further, as a configuration for moving the vanes 9 and 10 in the direction of the inner peripheral surface 1b of the cylinder 1, a pressure difference between the pressure on the tip end portions 9a and 10a side of the vanes 9 and 10 and the pressure on the inner peripheral side end portion side is determined. When the configuration to be used is used, the pressing force of the vanes 9 and 10 against the inner peripheral surface 1b of the cylinder 1 is reduced by controlling the pressure on the inner peripheral side end side, thereby further sliding resistance of the vane tip. It is also possible to reduce this.

Embodiment 2. FIG.
In the first embodiment, the compression element 101 is configured so that the longitudinal direction of the vanes 9 and 10 is substantially the same as the normal line of the inner peripheral surface 1 b of the cylinder 1. For example, the compression element 101 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. 6 is an enlarged view (bottom sectional view) of a main part showing the vicinity of a vane of a compression element according to Embodiment 2 of the present invention.
In FIG. 6, B indicates the mounting direction of the vane holding portion 6 a of the vane aligner 6 and the longitudinal direction of the vane 9. C represents the normal line of the arc of the tip 9a of the vane 9. That is, the vane holding portion 6a of the vane aligner 6 is attached to the end surface on the vane side in the central axis direction of the ring-shaped member of the vane aligner 6 so as to be inclined in the direction B. Thereby, the vane 9 is provided in the rotor part 4a of the rotor shaft 4 so that the longitudinal direction is inclined with respect to the normal line of the inner peripheral surface 1b of the cylinder 1. The normal C of the arc of the tip 9a of the vane 9 is inclined with respect to the vane longitudinal direction B, and the inner periphery of the cylinder 1 is inserted in a state where the vane holding portion 6a of the vane aligner 6 is inserted into the back groove 9b of the vane 9. It is comprised so that it may go to the center of the surface 1b. That is, the normal C of the arc of the tip 9 a of the vane 9 substantially matches the normal of the inner peripheral surface 1 b of the cylinder 1. The vane 9 and the vane aligner 5 and the vane 10 and the vane aligners 7 and 8 have the same configuration as described above.

  As described above, also in the vane type compressor 200 configured as in the second embodiment, the arc of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) and the inner peripheral surface 1b of the cylinder 1 are formed. It is possible to perform the compression operation in a state where the normals are always substantially coincident during rotation, and the same effect as in the first embodiment can be obtained. Further, as apparent from FIG. 6, in the second embodiment, the length of the arc of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) can be made longer than that in the first embodiment. The contact surface pressure between the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) and the inner peripheral surface 1b of the cylinder 1 can be reduced. Thereby, the sliding resistance of the vane front-end | tip part (The front-end | tip part 9a of the vane 9, the front-end | tip part 10a of the vane 10) can be reduced.

Embodiment 3 FIG.
In the first embodiment and the second embodiment, the vane 9 and the vane aligners 5 and 6 are configured separately, and the vane 10 and the vane aligners 7 and 8 are configured separately. Not limited to this, at least one of the vane aligners 5 and 6 may be formed integrally with the vane 9. Similarly, at least one of the vane aligners 7 and 8 may be configured integrally with the vane 10. In Embodiment 3, items that are not particularly described are the same as those in Embodiment 1 or Embodiment 2, and the same functions and configurations are described using the same reference numerals.

FIG. 7 is a perspective view showing a vane and a vane aligner of a compressor according to Embodiment 3 of the present invention. FIG. 7 shows a case where the vane 9 and the vane aligner 6 are integrally formed as an example of integrally configuring the vane and the vane aligner.
As can be seen from the first embodiment, the relative positional relationship between the rear groove 9b of the vane 9 and the vane holding portions 5a and 6a of the vane aligners 5 and 6 does not change in the operation of the vane compressor 200 (sealed type). Similarly, the relative positional relationship between the rear groove 10b of the vane 10 and the vane holding portions 7a and 8a of the vane aligners 7 and 8 does not change in the operation of the vane compressor 200 (sealed type). Therefore, it is possible to integrate both (vane 9 and vane aligners 5, 6 and vane 10 and vane aligners 7, 8). In the third embodiment, the vane 9 and the vane aligner 6 are manufactured separately, and the vane holding portion 6a of the vane aligner 6 is inserted into the rear groove 9b of the vane 9, and then both are fixed and integrally configured. Yes.

  In the third embodiment, the vane 9 and the vane aligner 6 are integrated. However, the vane aligner 5 may be integrated with the vane 9 or may not be integrated. That is, the same applies to the vane 9 and the vane 9 and at least one of the vane aligners 5 and 6 may be integrated. Similarly, the vane 10 and at least one of the vane aligners 7 and 8 may be integrated.

  Subsequently, the operation of the compression element 101 according to the third embodiment will be described. The compression element 101 according to the third embodiment performs the same operation as the compression element 101 shown in the first embodiment, but differs from the compression element 101 shown in the first embodiment in the following points. That is, at least one of the vane aligners 5 and 6 and the vane 9 are integrated, and at least one of the vane aligners 7 and 8 and the vane 10 are integrated, so that the vane 9 and the vane 10 are substantially centrifugally separated from the rotor portion 4a. Movement in the direction is fixed. Therefore, the tip 9 a of the vane 9 and the tip 10 a of the vane 10 do not slide with the inner peripheral surface 1 b of the cylinder 1, and the tip 9 a of the vane 9 and the tip 10 a of the vane 10 and the inner periphery of the cylinder 1 It rotates in a non-contact state (that is, a state in which a minute gap is maintained) between the surface 1b.

  As described above, in the vane type compressor 200 configured as in the third embodiment, the tip 9a of the vane 9 and the tip 10a of the vane 10 and the inner peripheral surface 1b of the cylinder 1 are not in contact with each other. There is no sliding loss of the vane tip (tip 9a of vane 9 and tip 10a of vane 10). Accordingly, the force acting on the sliding parts of the vane aligners 5 and 6 and the vane aligners 7 and 8 and the vane aligner holding parts 2a and 3a is increased, but in addition to the sliding part being in a fluid lubrication state, The sliding distance between the vane aligners 5, 6 and the vane aligners 7, 8 and the sliding portions of the vane aligner holding portions 2a, 3a is the sliding distance of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10). Therefore, the sliding loss can be further reduced as compared with the first embodiment.

  Also in the third embodiment, as in the second embodiment, the normal line of the arc of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) is set to the method of the inner peripheral surface 1b of the cylinder 1. The vane may be configured to have a constant inclination with respect to the normal direction of the inner circumferential surface 1b of the cylinder. Thereby, the arc length of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) can be increased, and the seal length increases to further increase the vane tip (vane 9). It is possible to reduce the leakage loss at the front end portion 9a and the front end portion 10a of the vane 10.

Embodiment 4 FIG.
In the first to third embodiments, recesses (back grooves 9b, 10b) are provided on the vane side, and protrusions (vane holding portions 5a, 6a, 7a, 8a) are provided on the vane aligner side. Connected with aligner. For example, the vane and the vane aligner may be connected as follows. In the fourth embodiment, items not particularly described are the same as those in the first to third embodiments, and the same functions and configurations are described using the same reference numerals.

  FIG. 8 is a plan view or a bottom view showing a vane aligner of a compression element according to Embodiment 4 of the present invention. FIG. 9 is a perspective view showing a vane of a compression element according to Embodiment 4 of the present invention. FIG. 10 is a side view showing a connection method between the vane and the vane aligner according to the fourth embodiment of the present invention. 8A shows a bottom view of the vane aligner 5 and a plan view of the vane aligner 6, and FIG. 8B shows a bottom view of the vane aligner 7 and a plan view of the vane aligner 8. Also, the two-dot chain line shown in FIG. 8A is the inner peripheral shape of the vane aligners 7 and 8, and the two-dot chain line shown in FIG. 8B is the inner peripheral shape of the vane aligners 5 and 6. FIG. 9A shows the vane 9 and FIG. 9B shows the vane 10.

  In the vane aligner 5 according to the fourth embodiment, slit-like vane holding grooves 5b are formed instead of the vane holding portions 5a of the vane aligner 5 shown in the first embodiment. In addition, the vane 9 according to the fourth embodiment is provided with a protruding portion 9c that is inserted into the vane holding groove 5b of the vane aligner 5 instead of the rear groove 9b of the vane 9 shown in the first embodiment. Yes. The distance between the outermost peripheral portion of the vane holding groove 5 b of the vane aligner 5 (that is, the protrusion 9 c of the vane 9) and the ring member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) It is slightly smaller than the radius of the circumference. Here, the protrusion 9c corresponds to the first protrusion in the present invention, and the vane holding groove 5b corresponds to the third recess in the present invention.

  Further, in the vane aligner 6 according to the fourth embodiment, slit-like vane holding grooves 6b are formed instead of the vane holding portions 6a of the vane aligner 6 shown in the first embodiment. Further, the vane 9 according to the fourth embodiment is provided with a protrusion 9d that is inserted into the vane holding groove 6b of the vane aligner 6 in place of the rear groove 9b of the vane 9 shown in the first embodiment. Yes. The distance between the outermost peripheral portion of the vane holding groove 6 b of the vane aligner 6 (that is, the protrusion 9 d of the vane 9) and the ring member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) It is slightly smaller than the radius of the circumference. Here, the protrusion 9d corresponds to the second protrusion in the present invention, and the vane holding groove 6b corresponds to the fourth recess in the present invention.

  Similarly, in the vane aligner 7 according to the fourth embodiment, a slit-like vane holding groove 7b is formed instead of the vane holding portion 7a of the vane aligner 7 shown in the first embodiment. In addition, the vane 10 according to the fourth embodiment is provided with a protruding portion 10c that is inserted into the vane holding groove 7b of the vane aligner 7 instead of the back surface groove 10b of the vane 10 shown in the first embodiment. Yes. Here, the protrusion 10c corresponds to the first convex portion in the present invention, and the vane holding groove 7b corresponds to the third concave portion in the present invention.

  Further, in the vane aligner 8 according to the fourth embodiment, a slit-like vane holding groove 8b is formed instead of the vane holding portion 8a of the vane aligner 8 shown in the first embodiment. Further, the vane 10 according to the fourth embodiment is provided with a protrusion 10d that is inserted into the vane holding groove 8b of the vane aligner 8 in place of the back surface groove 10b of the vane 10 shown in the first embodiment. Yes. Here, the protrusion 10d corresponds to the second protrusion in the present invention, and the vane holding groove 8b corresponds to the fourth recess in the present invention.

  As described above, the protrusion 9 c of the vane 9 is inserted into the vane holding groove 5 b of the vane aligner 5, and the protrusion 9 d of the vane 9 is inserted into the vane holding groove 6 b of the vane aligner 6. The direction is regulated so that the normal line of the arc always coincides with the normal line of the cylinder inner peripheral surface 1b. Similarly, the protrusion 10 c of the vane 10 is inserted into the vane holding groove 7 b of the vane aligner 7, and the protrusion 10 d of the vane 10 is inserted into the vane holding groove 8 b of the vane aligner 8. The direction is regulated so that the normal line always coincides with the normal line of the cylinder inner peripheral surface 1b.

  As described above, also in the vane type compressor 200 configured as in the fourth embodiment, the arc of the vane tip (the tip 9a of the vane 9 and the tip 10a of the vane 10) and the inner peripheral surface 1b of the cylinder 1 are formed. It is possible to perform the compression operation in a state where the normals are always substantially coincident during rotation, and the same effect as in the first embodiment can be obtained.

  In the fourth embodiment, the vane holding grooves 5b and 6b of the vane aligners 5 and 6 are opened to the inner peripheral side. However, the inner peripheral side is not opened but a stopper is used, and the vane 9 is the cylinder 1 The excessive movement in the direction opposite to the inner peripheral surface 1b side may be restricted. The vane 10 and the vane aligners 7 and 8 may have the same configuration. With the above configuration, the same effect as in the first embodiment can be obtained.

  In the fourth embodiment, the vane 9 and at least one of the vane aligners 5 and 6 may be integrated, or the vane 10 and at least one of the vane aligners 7 and 8 may be integrated. The same effect as in the third mode can be obtained.

  Further, the protrusions (protrusions 9c, 9d, 10c, and 10d) provided on the end surface of the vane (vanes 9 and 10) are attached to be inclined with respect to the normal line of the inner peripheral surface 1b of the cylinder 1, and the vane tip (vane 9) is attached. If only the arcs of the tip 9a and the tip 10a) of the vane 10 are configured so that their normal lines coincide with the normal direction of the cylinder inner peripheral surface 1b, the same effect as in the second embodiment can be obtained.

Embodiment 5 FIG.
Of course, the present invention can also be implemented in a vane type compressor having three or more vanes. In the fifth embodiment, items not particularly described are the same as those in the first to fourth embodiments, and the same functions and configurations are described using the same reference numerals. In the fifth embodiment, an example in which three vanes (vanes 9, 10, and 32) are provided in the vane compressor 200 shown in the first embodiment will be described.

  FIG. 11 is a longitudinal sectional view showing a vane type compressor according to Embodiment 5 of the present invention. FIG. 12 is a plan view or a bottom view showing the vane aligner provided in the compression element of the vane type compressor. FIG. 11 shows a longitudinal sectional view at the position of the third vane 32. 12 (a) shows a bottom view of the vane aligner 7 and a plan view of the vane aligner 8. FIG. 12 (b) shows a bottom view of the vane aligner 5 and a plan view of the vane aligner 6. FIG. ) Shows a bottom view of the vane aligner 30 and a plan view of the vane aligner 31. 12 (a) is the inner peripheral shape of the vane aligners 5 and 6 and the vane aligners 30 and 31, and the two-dot chain line shown in FIG. 12 (b) is the vane aligners 7 and 8 and the vane aligner. The two-dot chain lines shown in FIG. 12C are the inner peripheral shape of the vane aligners 5 and 6 and the vane aligners 7 and 8.

  The vane type compressor 200 according to the fifth embodiment includes a vane 32 in addition to the vanes 9 and 10. The installation structure of the vane 32 on the rotor portion 4a is the same as that of the vanes 9 and 10. Further, the vane compressor 200 according to the fifth embodiment is connected to the vane 32. Vane aligners 30 and 31 are provided.

  More specifically, the vane aligner 30 includes a ring-shaped member and a vane holding portion 30a erected on one end surface (lower side in FIG. 11) in the central axis direction of the ring-shaped member. The vane holding part 30a is, for example, a plate-like protrusion having a substantially square cross section. In the fifth embodiment, the vane holding portion 30a is formed in the normal direction of the ring-shaped member. Further, the distance between the outermost peripheral portion of the vane holding portion 30 a and the ring member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) is slightly smaller than the radius of the inner peripheral portion of the vane aligner 5. (See FIG. 12). Here, the vane aligner 30 corresponds to the first vane aligner in the present invention, and the vane holding portion 30a corresponds to the third convex portion in the present invention.

  The vane aligner 30 is overlapped with the vane aligners 5 and 7 and inserted into the vane aligner holding portion 2 a of the frame 2. At this time, the vane aligner 30 is disposed on the uppermost portion (the side farthest from the vane). The vane aligner 30 is connected to the vane 32 by inserting the vane holding portion 30 a into the back surface groove 32 b (first recess) of the vane 32. Here, even when three or more vanes are provided, as long as the vane holding portion of the vane aligner provided at the upper portion is disposed inside the inner peripheral portion of the vane aligner provided at the lower portion, each vane aligner and the vane aligner are connected to them. It is possible to prevent the generated vanes from interfering with each other. In other words, in order to prevent the vane aligners and the vanes connected thereto from interfering with each other, in the adjacent vane aligner, the radius of the inner peripheral portion of the ring-shaped member of the vane aligner arranged on the side close to the vane is The distance between the outermost peripheral portion of the vane holding portion of the vane aligner disposed on the side far from the vane and the central axis of the ring-shaped member (that is, the central axis of the inner peripheral surface of the cylinder 1) may be larger.

  The vane aligner 31 includes a ring-shaped member and a vane holding portion 31a provided upright on one end surface (upper side in FIG. 11) in the central axis direction of the ring-shaped member. The vane holding part 31a is, for example, a plate-like protrusion having a substantially square cross section. In the fifth embodiment, the vane holding portion 31a is formed in the normal direction of the ring-shaped member. Further, the distance between the outermost peripheral portion of the vane holding portion 31 a and the ring-shaped member central axis (that is, the central axis of the inner peripheral surface of the cylinder 1) is slightly smaller than the radius of the inner peripheral portion of the vane aligner 6. (See FIG. 12). Here, the vane aligner 31 corresponds to the second vane aligner in the present invention, and the vane holding portion 31a corresponds to the fourth convex portion in the present invention.

  The vane aligner 31 is overlapped with the vane aligners 6 and 8 and is inserted into the vane aligner holding portion 3 a of the cylinder head 3. At this time, the vane aligner 31 is disposed at the lowermost portion (the side farthest from the vane). The vane aligner 31 is connected to the vane 32 by inserting the vane holding portion 31 a into the rear groove 32 b (second recess) of the vane 32. Here, even when three or more vanes are provided, as long as the vane holding portion of the vane aligner provided in the lower portion is disposed inside the inner peripheral portion of the vane aligner provided in the upper portion, each vane aligner and the connection with them are connected. It is possible to prevent the generated vanes from interfering with each other. In other words, in order to prevent the vane aligners and the vanes connected thereto from interfering with each other, in the adjacent vane aligner, the radius of the inner peripheral portion of the ring-shaped member of the vane aligner arranged on the side close to the vane is The distance between the outermost peripheral portion of the vane holding portion of the vane aligner disposed on the side far from the vane and the central axis of the ring-shaped member (that is, the central axis of the inner peripheral surface of the cylinder 1) may be larger.

  As described above, also in the vane type compressor 200 configured as in the fifth embodiment, the compression operation is performed in a state where the arc of the vane tip and the normal line of the inner peripheral surface 1b of the cylinder 1 are substantially coincided with each other during rotation. Therefore, the same effects as those of the first embodiment can be obtained.

  Also in the fifth embodiment, as in the second embodiment, the normal line of the arc of the vane tip is substantially coincident with the normal line of the inner peripheral surface 1b of the cylinder 1, and the vane longitudinal direction is the cylinder inner peripheral surface 1b. You may comprise so that it may have a fixed inclination with respect to the normal line direction. As a result, the arc length of the vane tip can be increased, and the leakage length at the vane tip can be further reduced by increasing the seal length.

  Also in the fifth embodiment, the vane 9 and at least one of the vane aligners 5 and 6 may be integrated, or the vane 10 and at least one of the vane aligners 7 and 8 may be integrated, The vane 32 and at least one of the vane aligners 30 and 31 may be integrated, and the same effect as in the third embodiment is obtained.

  1 cylinder, 1a suction port, 1b inner peripheral surface, 2 frame, 2a vane aligner holding part, 2b bearing part, 2c discharge port, 3 cylinder head, 3a vane aligner holding part, 3b bearing part, 4 rotor shaft, 4a rotor part 4b Rotating shaft portion, 4c Rotating shaft portion, 4d Bush holding portion, 4e Bush holding portion, 4f Vane relief portion, 4g Vane relief portion, 5 vane aligner, 5a vane holding portion, 5b vane holding groove, 6 vane aligner, 6a Vane holding portion, 6b Vane holding groove, 7 vane aligner, 7a Vane holding portion, 7b Vane holding groove, 8 vane aligner, 8a Vane holding portion, 8b Vane holding groove, 9 vane, 9a tip, 9b Back groove, 9c Projection Part, 9d protrusion part, 10 vane, 10a tip part, 10b rear groove, 10c Projection, 10d Projection, 11 Bush, 12 Bush, 13 Suction chamber, 14 Intermediate chamber, 15 Compression chamber, 21 Stator, 22 Rotor, 23 Glass terminal, 24 Discharge pipe, 25 Refrigerating machine oil, 26 Suction unit, 30 vane aligner, 30a vane holding part, 31 vane aligner, 31a vane holding part, 32 vane, 32b rear groove, 101 compression element, 102 electric element, 103 airtight container, 200 vane type compressor.

Claims (7)

A cylinder in which a cylindrical through hole is formed;
A frame that closes one open end of the through hole of the cylinder;
A cylinder head for closing the other open end of the through hole of the cylinder;
A cylindrical rotor portion that rotates about a rotation axis that is shifted from the central axis of the through hole by a predetermined distance inside the cylinder, and a rotor shaft that has a shaft portion that transmits a rotational force to the rotor portion;
A plurality of vanes 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 type compressor having
The vane is supported by the rotor portion so as to be swingable and movable in a substantially centrifugal direction,
A first concave portion or a first convex portion is formed on a surface of the vane facing the frame,
A second concave portion or a second convex portion is formed on a surface of the vane facing the cylinder head,
A third convex portion inserted into the first concave portion of the corresponding vane or a third concave portion into which the first convex portion of the corresponding vane is inserted is formed, and the third convex portion or A plurality of first vane aligners provided on the frame such that the third recess is rotatable about the central axis of the through hole of the cylinder;
A fourth convex portion inserted into the second concave portion of the corresponding vane or a fourth concave portion into which the second convex portion of the corresponding vane is inserted is formed, and the fourth convex portion or A plurality of second vane aligners provided in the cylinder head such that the fourth recess is rotatable about the central axis of the through hole of the cylinder;
With
Each of the plurality of first vane aligners can be rotated without interference between the third convex portion of each other or the first convex portion inserted into the third concave portion of each other. Provided in the frame;
Each of the plurality of second vane aligners is rotatable so that the fourth protrusions inserted into each other or the second protrusions inserted into the respective fourth recesses do not interfere with each other. A vane type compressor provided in the cylinder head. The plurality of first vane aligners includes:
The third convex portion or the third concave portion is formed on a ring-shaped member, and the ring-shaped member is stacked in the direction of the central axis of the through hole to be a vane aligner holding portion of the frame. Placed in
The adjacent first vane aligner is
The radius of the inner peripheral portion of the ring-shaped member of the first vane aligner disposed on the side close to the vane is the third convex portion of the first vane aligner disposed on the side far from the vane. Alternatively, the vane type compressor according to claim 1, wherein the vane type compressor is larger than a distance between an outermost peripheral portion of the third recess and the central axis of the through hole. The plurality of second vane aligners includes:
The fourth convex portion or the fourth concave portion is formed on a ring-shaped member, and these ring-shaped members are stacked in the direction of the central axis of the through hole to hold the vane aligner of the cylinder head. Placed in the
The adjacent second vane aligner is
The radius of the inner peripheral part of the ring-shaped member of the second vane aligner arranged on the side close to the vane is the fourth convex part of the second vane aligner arranged on the side far from the vane. The vane compressor according to claim 1 or 2, wherein a distance between the outermost peripheral portion of the fourth recess and the central axis of the through hole is larger.   The radius of the circular arc shape of the said front-end | tip part of the said several vane and the radius of the internal peripheral surface of the said cylinder are substantially the same radius, The Claim 1 characterized by the above-mentioned. Vane type compressor.   5. The apparatus according to claim 1, wherein at least one of the plurality of first vane aligners and the plurality of second vane aligners is configured integrally with the corresponding vane. The vane type compressor according to item. The rotor portion is formed with a substantially cylindrical bush holding portion penetrating in the rotation axis direction,
A pair of substantially semicircular bushes are inserted into these bush holding portions,
The said vane is supported by being able to rock | fluctuate and to move to a substantially centrifugal direction by the said rotor part by being pinched | interposed and supported by the said bush. The vane type compressor according to one item. The vane is
The longitudinal direction has a predetermined inclination with the normal direction of the inner peripheral surface of the cylinder,
7. The rotor portion according to claim 1, wherein the rotor portion is provided so that a normal direction of the arc shape of the tip portion substantially coincides with a normal line of the inner peripheral surface of the cylinder. The vane type compressor described in 1.

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