JP2013217347A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem that a conventional vane rotary compressor involves a large mechanism and a large loss when a vane rotates around a center axis line of a tubular cylinder chamber, the mechanism is complicate, an eccentric amount of a center axis line of a rotor shaft to the center axis line of the cylinder chamber is large, and a compression chamber capacity cannot be increased easily.SOLUTION: A vane is provided with a vane aligner which controls a longitudinal direction of a vane to substantially match with a normal direction of an inner peripheral face of a cylinder and revolves around a periphery of a rotation axis part by rotary motion of a rotor part. It is further provided with a recess part so that neither the vane aligner nor the rotation axis part contacts with the rotation axis part.

Description

  The present invention relates to a vane type compressor.

  In recent years, the use of a refrigerant having a low global warming potential (hereinafter referred to as GWP) has been studied as a countermeasure against global warming. However, many low GWP refrigerants have a lower operating pressure than conventional refrigerants, requiring a large amount of refrigerant circulation in the refrigeration cycle. As a compressor for controlling the circulation amount of the refrigeration cycle, a large displacement amount is required, and it is essential to enlarge the compression element portion. On the other hand, in a car air conditioner or the like where the use of a low GWP refrigerant is advanced, a vane rotary compressor that uses a refrigerant with a low operating pressure and can realize space saving is used.

  A conventional vane type compressor has a rotor shaft provided in a cylindrical inner space of a cylinder, that is, a cylinder chamber (a cylindrical rotor portion that rotates in the cylinder and a shaft that transmits rotational force to the rotor portion are integrated. A rotor shaft), a vane groove formed in one or a plurality of locations in the rotor portion of the rotor shaft, and a vane fitted in the vane groove, and formed by the cylinder, the rotor portion, and the vane. The refrigerant is sucked into the compression chamber, and the volume of the compression chamber is changed along with the rotation of the rotor shaft and the sliding of the vane to compress the refrigerant. At that time, the tip of the vane slides while coming into contact with the inner circumferential surface of the cylinder (see, for example, Patent Document 1).

  As another example, the interior of the rotor shaft is configured to be hollow, and a vane fixed shaft is disposed therein. The vane is rotatably attached to the fixed shaft, and further, a semicircle is disposed near the outer diameter of the rotor portion. There has also been proposed a vane type compressor in which a vane is rotatably held with respect to a rotor portion via a pair of rod-shaped clamping members (see, for example, Patent Document 2).

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

  For example, in a general vane type compressor such as Patent Document 1, the direction in which the vane is pushed from the rotor portion to the inner peripheral surface of the cylinder chamber, that is, the cylinder inner peripheral surface is regulated by the vane groove of the rotor portion. It is held so as to always have the same inclination with respect to the outer peripheral surface of the part. As the rotor shaft rotates, the angle between the vane and the inner peripheral surface of the cylinder changes because the tip of the vane contacts the inner peripheral surface of the cylinder over the entire circumference. It was necessary to make it smaller than R.

  However, in the case where the vane tip slides while abutting against the cylinder inner peripheral surface, the cylinder inner peripheral surface and the vane tip which are greatly different from each other slide, so an oil film is formed between the two parts (cylinder and vane). However, it does not enter the state of fluid lubrication that slides through the oil film, but enters the boundary lubrication state. In general, the friction coefficient according to the lubrication state is about 0.001 to 0.005 in the fluid lubrication, but is very large at about 0.05 or more in the boundary lubrication state.

  Therefore, sliding resistance between the vane tip and the cylinder inner peripheral surface in the boundary lubrication state increases the sliding resistance, resulting in a significant decrease in compressor efficiency due to an increase in mechanical loss. There was a problem that the surface was easily worn and it was difficult to ensure a long life.

  As a form of improvement, as in Patent Document 2, a hollow rotor portion is provided with a fixed shaft that rotatably supports a vane in a cylindrical inner space of the cylinder, that is, a central axis of the cylinder chamber, and the vane has There is a method of holding a vane via a pinching member in the vicinity of the outer peripheral portion of the rotor portion so that it can rotate together with the rotor portion.

  In this configuration, since the vane is rotatably supported by the center axis of the cylinder chamber, the direction in which the vane is pushed from the rotor portion to the cylinder inner peripheral surface is always the normal direction of the cylinder inner peripheral surface, and the vane tip portion Moves along the inner circumferential surface of the cylinder. That is, when the vane rotates around the central axis of the cylinder chamber, the vane is pushed out from the rotor portion in the normal direction of the cylinder inner peripheral surface. Therefore, R on the inner circumferential surface of the cylinder and R on the tip of the vane can be substantially matched, and the vane tip and the inner circumferential surface of the cylinder can be configured in a non-contact manner. For example, even when the vane tip and the cylinder inner peripheral surface come into contact with each other, a fluid lubrication state with a sufficient oil film can be achieved. 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, in the configuration in which the rotor portion is hollow, it is difficult to apply a rotational force to the rotor portion and to support the rotation of the rotor portion. End plates are provided on both end faces of the hollow rotor portion, and a shaft that transmits a rotational force for rotating the rotor portion, that is, a rotating shaft is connected to the center of one end plate, and is supported rotatably around the rotating shaft. The other end plate must be formed in a ring shape with a hole in the center so that the rotation range of the vane fixing shaft or the vane shaft support member does not interfere with the rotation support portion of the end plate. . For this reason, the part which rotationally supports the end plate needs to be configured to have a larger diameter than the rotating shaft, and there is a problem that sliding loss increases. That is, there is a problem that the loss is large and the size is increased.

  Further, in order to use the vane type compressor for an air conditioner having a larger refrigerating capacity, it is necessary to increase the compression chamber volume, that is, increase the displacement of the compression element. In particular, in order not to increase the size of the air conditioner, it is necessary to increase the displacement without increasing the size of the compressor. In addition, even in a conventional air conditioner, if the displacement of the compressor is large, the number of revolutions can be reduced and noise and efficiency can be improved. Therefore, in order to increase the displacement of the compression element without increasing the outer shape of the compression element, that is, the cylinder, the outer diameter of the rotor portion is decreased and the eccentric amount of the central axis of the rotor shaft with respect to the central axis of the cylinder chamber is increased. We have to go. However, in the configuration of the conventional vane type compressor, if the amount of eccentricity of the center axis of the rotor shaft with respect to the center axis of the cylinder chamber is increased, the vane fixing shaft cannot be disposed in the hollow space of the rotor portion. Alternatively, when the hollow space of the rotor portion is enlarged so as to include the central axis of the cylinder chamber, there is a problem in terms of dimensionality that the rotor portion cannot be formed because there is no thickness separating the outer peripheral portion of the rotor portion from the hollow space. That is, there is a problem that it is not easy to increase the volume of the compression chamber by increasing the amount of eccentricity of the central axis of the rotor shaft with respect to the central axis of the cylinder chamber in order to be mounted on a larger air conditioner.

  The present invention has been made to solve the above-described problems, and has a plate-like shape and is arranged in the rotor portion so that the longitudinal direction thereof is substantially the radial direction of the rotor portion, and the circumference of the rotor portion. The vane held in the rotor part so as to be rotatable in the direction and movable in the almost radial direction of the rotor part partitions the space formed by the outer peripheral surface of the rotor part and the inner peripheral surface of the cylinder to form a compression chamber, In a compressor in which the vane moves in the cylinder circumferential direction in a state where the longitudinal direction of the vane and the normal direction of the inner peripheral surface of the cylinder substantially coincide with each other, the center of the rotor shaft with respect to the central axis of the cylinder chamber The purpose is to obtain a large-capacity compressor in which the amount of eccentricity of the axis is increased and the volume of the compression chamber is increased.

The vane type compressor according to the present invention is substantially cylindrical and has a cylinder that is open at both ends in the axial direction, a cylinder head that closes one opening of the cylinder, and a frame that closes the other opening of the cylinder. And a rotor shaft having a cylindrical rotor portion that rotates in a center axis that is eccentric with the center axis of the cylinder in the cylinder, and a rotary shaft portion that is provided on the center axis of the rotor portion and transmits a rotational force to the rotor portion. The rotor part has a plate shape and is arranged in the rotor part so that its longitudinal direction is substantially the radial direction of the rotor part, and is rotatable in the circumferential direction of the rotor part and movable in the substantially radial direction of the rotor part In the vane type compressor that forms the compression chamber by partitioning the space formed by the vane held by the vane and the outer peripheral surface of the rotor portion and the inner peripheral surface of the cylinder by the vane,
The vane is provided with a vane aligner that is controlled so that the longitudinal direction of the vane and the normal direction of the inner peripheral surface of the cylinder substantially coincide with each other and rotates around the rotating shaft portion by the rotational movement of the rotor portion. A vane type compressor provided with a relief part that does not contact the rotating shaft part.

  The vane type compressor according to the present invention is configured such that a vane aligner that rotates around the rotating shaft portion by the rotational movement of the rotor portion is regulated so that the longitudinal direction of the vane and the normal direction of the inner peripheral surface of the cylinder substantially coincide with each other. In order to prevent the vane aligner from coming into contact with the rotary shaft portion, the rotary shaft portion is provided with a relief portion, so that the eccentric amount of the central axis of the rotor shaft with respect to the central axis of the cylinder chamber is increased, and the volume of the compression chamber is expanded. A large capacity compressor can be obtained.

It is a longitudinal cross-sectional view of the vane type compressor which concerns on Embodiment 1 of this invention. It is a disassembled perspective view of the compression element of the vane type compressor which concerns on Embodiment 1 of this invention. It is a cross-sectional view of the compression element of the vane type compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of the compression operation | movement of the vane type compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing explaining the effect | action of the rotor shaft small diameter part of the vane type compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of the dimension comparison of the compression element component of the vane type compressor which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view of the vane type compressor which concerns on Embodiment 2 of this invention. It is a perspective view of the vane aligner of the vane type compressor which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
FIG. 1 shows the first embodiment, and is a longitudinal sectional view of a vane compressor. A vane type compressor (sealed type) will be described with reference to FIG. However, this embodiment is characterized by the compression element, and the vane type compressor (sealed type) is an example. The present embodiment is not limited to a sealed type, but can be applied to other configurations such as an engine drive and an open container. In the present embodiment, the case where there are two vanes is shown, but one or three or more vanes may be used.

  The compressor shown in the present embodiment is mainly used for the purpose of compressing and circulating a refrigerant for refrigeration and air conditioning. In particular, in the configuration having two or more vanes, the volume flow rate of the circulating refrigerant is large with respect to the size of the cylinder, so that it is suitable for a low-pressure refrigerant requiring a relatively large refrigerant flow rate. The type of refrigerant is suitable for refrigerants such as R600a (isobutane), R600 (butane), R290 (propane), R134a, R152a, R161, R407C, R1234yf, R1234ze, etc., having a normal boiling point of −45 ° C. or higher.

  A vane type compressor (sealed type) 100 shown in FIG. 1 contains a compression element 101 and an electric element 102 that drives the compression element 101 in a hermetic container 103. The compression element 101 is located at the bottom of the sealed container 103, and refrigerating machine oil (not shown) stored in the bottom of the sealed container 103 is guided to the compression element 101 by an oil supply mechanism (not shown) in the compression element 101. Each sliding part of the compression element 101 is lubricated.

  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 11 fixed to the inner periphery of the hermetic container 103, and a rotor 12 disposed inside the stator 11 and having a permanent magnet.

The stator 11 includes a stator core, an insulating member, and a coil, and a lead wire 15 is connected to the coil. The lead wire 15 is connected to the glass terminal 13 fixed to the sealed container 103 by welding, and power is supplied from the glass terminal 13. An external power supply for supplying power to the coil of the stator 11 is connected to the glass terminal 13 via a lead wire 15. The coil is wound in the direction of the rotation axis through an insulating member made of polyethylene terephthalate (PET), polyethylene naphthalate (PEN), or the like, on a plurality of teeth provided on the stator core. With such a configuration, when an external power source energizes the coil, the coil generates a magnetic flux and generates a plurality of magnetic poles on the stator core.
The stator core is formed by laminating core sheets obtained by punching thin electromagnetic steel plates, and is fixed to the sealed container 103 by shrink fitting.

The rotor 12 is provided with a rotor core formed by laminating iron core sheets punched out of thin electromagnetic steel plates in the same manner as the stator 11 and a magnet insertion hole in the vicinity of the outer peripheral surface of the rotor core. Permanent magnets such as ferrite magnets and rare earth magnets are inserted into the magnet insertion holes to form magnetic poles on the rotor 12.
The permanent magnet may be a single ferrite magnet or rare earth magnet, or a mixture of ferrite magnets and rare earth magnets. In addition, the magnet insertion hole has been described as near the outer peripheral surface of the rotor core, but it is provided on the inner peripheral side of the rotor core at a predetermined distance from the outer peripheral surface of the rotor core in order to adjust the magnetic force of the permanent magnet. It doesn't matter. Moreover, you may affix on the outer peripheral surface of a rotor core, without providing a magnet insertion hole in a rotor core.
In addition, the rotating shaft 4b of the rotor shaft 4 is fastened to the center of the rotor core by shrink fitting or the like.

  With the above-described configuration, the electric element 102 rotates the rotor 12 by the action of the magnetic flux generated by the permanent magnet of the rotor 12 and the magnetic flux generated by the coil of the stator 11, and transmits the rotational force to the rotor shaft 4. And transmitted to the compression element 101 via the rotor shaft 4.

  In addition, although the electric element 102 demonstrated as an example the brushless DC motor, the induction motor which does not use a permanent magnet for the rotor 12 may be sufficient, for example. The structure of the stator of the induction motor is almost the same as that of the brushless DC motor, but the rotor is provided with a secondary coil instead of a permanent magnet, and the stator side coil is the rotor side secondary coil. The magnetic flux is induced to generate a rotational force, and the rotor 12 is rotated.

  The compression element 101 sucks and compresses low-pressure refrigerant from a suction pipe (not shown) into the compression chamber, and the compressed refrigerant is discharged into the sealed container 103 and passes through the electric element 102 to be sealed. Is discharged to the outside (high pressure side of the refrigeration cycle) from a discharge pipe 14 fixed to the top of the refrigeration. Although the high-pressure type in which the inside of the hermetic container 103 has a high pressure has been described, the vane compressor 200 is a low-pressure type in which the inside of the hermetic container 103 has a low pressure even though the inside of the hermetic container 103 has a high pressure. It does not matter.

  Since the present embodiment is characterized by the compression element 101, the compression element 101 will be described in detail below. Also in FIG. 1, reference numerals are attached to the components constituting the compression element 101. However, the exploded perspective view of FIG. 2 is easier to understand, so that FIG. 1 and FIG. 3 will be described. FIG. 2 is a diagram showing the first embodiment, and is an exploded perspective view of the compression element 101 of the vane compressor. FIG. 3 is a cross-sectional view (top view) of the compression element 101 cut along the Z-Z ′ plane of FIG. 1. Reference numerals in parentheses in FIG. 3 are reference numerals of parts hidden behind the upper part.

As shown in FIG. 2, the compression element 101 has the following elements.
(1) Cylinder 1: The overall shape is substantially cylindrical, and has an internal space that is open at both ends in the axial direction, that is, a cylinder chamber 1a. A suction port 1c is opened on the inner peripheral surface 1b of the cylinder chamber 1a, and the suction port 1c is connected to a suction pipe connected to a refrigerant circuit outside the sealed container 103. Similarly, a discharge flow path 1d connected to a discharge port 2c described later is provided on the inner peripheral surface 1b, and the discharge port 2c and the cylinder chamber 1a communicate with each other;
(2) Frame 2: The cross section is substantially T-shaped, the portion in contact with the cylinder 1 is substantially disk-shaped, and closes one opening (upper side in FIG. 2) of the cylinder 1. The end face of the frame 2 on the cylinder 1 side is provided with a substantially cylindrical recess 2a (shown only in FIG. 1) concentric with the central axis of the cylinder chamber 1a and having an inner diameter smaller than the inner diameter of the cylinder chamber 1a. The recess 2a is open to the cylinder chamber 1a side, and vane aligner portions 5b and 6b, which will be described later, are fitted therein and pressed against the inner peripheral surface of the recess 2a. Moreover, a substantially cylindrical bearing portion 2b is provided on the side opposite to the side in contact with the cylinder 1, and the internal space of the bearing portion 2b communicates with the recess 2a. A rotating shaft 4b of the rotor shaft 4 to be described later is inserted and held rotatably. The central axis of the bearing 2b is provided at a position that is eccentric with respect to the central axis of the cylinder chamber 1a, and the rotary shaft 4b of the rotor shaft 4 is eccentric with respect to the central axis of the cylinder chamber 1a. Perform a rotational movement on the line. Further, the frame 2 is provided with a discharge port 2c that communicates from the end surface on the cylinder 1 side to the bearing portion 2b side;
(3) Cylinder head 3: The cross section is substantially T-shaped, the portion in contact with the cylinder 1 is substantially disk-shaped, and the opening of the cylinder 1 opposite to the side closed by the frame 2 ( The lower side in FIG. 2 is closed. A cylindrical recess 3a having an inner diameter smaller than the inner diameter of the cylinder chamber 1a is provided on the cylinder 1 side end surface of the cylinder head 3 and is concentric with the central axis of the cylinder 1. The recessed part 3a is opened to the cylinder chamber 1a side, and vane aligner parts 5c and 6c described later are fitted into the recessed part 3a and pressed against the inner peripheral surface of the recessed part 2a. Further, a substantially cylindrical bearing portion 3b is provided on the side opposite to the side in contact with the cylinder 1, and the inner space of the bearing portion 3b communicates with the recess 3a, and a rotating shaft portion 4c of the rotor shaft 4 to be described later. Is inserted and held rotatably. The central axis of the bearing portion 3b is provided at a position eccentric with respect to the central axis of the cylinder chamber 1a, and the rotary shaft 4c of the rotor shaft 4 is eccentric with respect to the central axis of the cylinder chamber 1a. Perform rotational movement on the line;
(4) Rotor shaft 4: Rotor portion 4a that performs rotational motion on a central axis that is eccentric from cylinder chamber 1a in cylinder 1, and rotary shaft portions 4b and 4c that are provided above and below the central axis of rotor portion 4a. Is a united structure. The rotor portion 4a is provided with bush holding portions 4d and 4e and vane relief portions 4f and 4g that are substantially circular in cross section perpendicular to the axial direction of the rotor portion 4a and penetrate in the axial direction of the rotor portion 4a. The bush holding portion 4d is provided on the outer peripheral side of the rotor portion 4a, and the vane escape portion 4f is provided on the central axis side of the rotor portion 4a of the bush holding portion 4d so as to communicate with the bush holding portion 4d in the radial direction. Similarly, the bush holding portion 4e is provided on the outer peripheral side of the rotor portion 4a, and the vane relief portion 4g is provided on the central axis side of the rotor portion 4a of the bush holding portion 4e so as to communicate with the bush holding portion 4e in the radial direction. ing. The bush holding portions 4d and 4e are opened on the outer peripheral surface 4k of the rotor portion 4a. Further, the rotating shaft portion 4b of the rotor shaft 4 has a vane aligner portion relief portion at a position overlapping with vane aligner portions 5b and 6b, which will be described later, in an axial direction, that is, where the vane aligner portions 5 and 6b go around. Is provided. In this example, the relief portion is formed by a narrow diameter portion 4h having a diameter smaller than that of the rotating shaft portion. Similarly, the rotating shaft portion 4c of the rotor shaft 4 also escapes the vane aligner portion at a position where it overlaps with vane aligner portions 5c, 6c, which will be described later, that is, where the vane aligner portions 5c, 6c go around. Is provided. In this example, the relief part is formed by a narrow diameter part 4j (shown only in FIG. 1) whose diameter is smaller than that of the rotating shaft part;
(5) Vane 5, 6: At least one or more vanes are provided in the rotor portion 4a. Here, an example in which two vanes, the first vane 5 and the second vane 6, are provided will be described. The vane 5 includes a plate-like vane portion 5a having a substantially rectangular parallelepiped shape and vane aligner portions 5b and 5c having a partial ring shape, that is, an arc shape, provided on an end surface of the vane portion 5a. The vane portion 5a is attached to the rotor portion 4a so that the plate-like longitudinal direction is the radial direction of the rotor portion 4a, and the vane on the cylinder inner peripheral surface 1b side opposite to the center side of the rotor portion 4a. 5 d of front-end | tip parts, the vane back surface part 5e by the side of the central axis of the rotor part 4a, the axial direction of the rotor part 4a, the side part 5f by the side of the frame 2, the axial direction of the rotor part 4a, and the side part 5g by the side of the cylinder head 3 And side portions 5h and 5j in the circumferential direction of the rotor portion 4a. A vane aligner portion 5b is provided on the vane back surface portion 5e side of the side surface portion 5f in the axial direction of the vane portion 5a. Similarly, a vane aligner portion 5c is provided on the vane back surface portion 5e side of the side surface portion 5g in the axial direction of the vane portion 5a. The vane portion 5a is substantially the central portion of the vane aligner portions 5b and 5c, and the longitudinal direction of the vane portion 5a is perpendicular to the arc-shaped outer peripheral surface of the vane aligner portions 5b and 5c, that is, the normal direction. The tip 5d is provided so as to be directed in the opposite direction to the center of the arc of the vane aligner 5b, 5c, that is, outward. Similarly, the vane 6 is composed of a substantially rectangular plate-like vane portion 6a and partial ring-shaped, that is, arc-shaped vane aligner portions 6b and 6c provided on the end face of the vane portion 6a. The vane portion 6a is attached to the rotor portion 4a so that the plate-like longitudinal direction is the radial direction of the rotor portion 4a, and the vane on the cylinder inner peripheral surface 1b side opposite to the center side of the rotor portion 4a. 6 d of tip part, vane back part 6e by the side of the central axis of rotor part 4a, axial direction of rotor part 4a, side part 6f by the side of frame 2, axial direction of rotor part 4a, side part 6g by the side of cylinder head 3 And side portions 6h, 6j in the circumferential direction of the rotor portion 4a. A vane aligner portion 6b is provided on the vane back surface portion 6e side of the side surface portion 6f in the axial direction of the vane portion 6a. Similarly, a vane aligner portion 6c is provided on the vane back surface portion 6e side of the side surface portion 6g in the axial direction of the vane portion 6a. The vane portion 6a is substantially the central portion of the vane aligner portions 6b and 6c, and the longitudinal direction of the vane portion 6a is a direction orthogonal to the arcuate outer peripheral surface of the vane aligner portions 6b and 6c, that is, a normal direction. The front end portion 6d is provided so as to be directed in the opposite direction to the center of the arc of the vane aligner portions 6b and 6c, that is, outward. The outer diameter of the vane aligner portions 5b, 5c, 6b, 6c, that is, the radius from the central axis side of the rotor portion 4a to the vane tip portions 5d, 6d side of the vane aligner portions 5b, 5c, 6b, 6c is The recesses 2a and 3a formed in the cylinder head 3 are configured to have substantially the same radius as the inner diameter, and the vane aligner portions 5b and 6b are rotatably fitted in the recess 2a, and the vane aligner portions 5c and 6c are rotatably fitted in the recess 3a. The Further, the inner diameter side of the vane aligner portions 5b, 5c, 6b, 6c is inside the outer diameter of the rotating shaft portions 4b, 4c in the rotational phase closest to the rotor shaft 4, and does not contact the small diameter portions 4h, 4j. Configured as follows. It should be noted that the axial dimension or height of the vane aligner portions 5b, 5c, 6b and 6c is the same as the axial dimension or height of the small diameter portions 4h and 4j of the rotor shaft 4. The vane tip portions 5d and 6d located on the cylinder inner peripheral surface 1b side of the vane portions 5a and 6a are formed in an arc shape on the outer side, and the radius of the arc shape is substantially equal to the radius of the cylinder inner peripheral surface 1b. Has been. In addition, the vane aligner portion in the case of a single vane may have a ring shape having substantially the same radius as the inner diameter of the recesses 2a and 3a;
(6) Bushings 7 and 8: In this embodiment, one pair is used for each of the vanes 5 and 6, and the first bushing corresponding to the first vane 5 is 7 and the second vane 6 corresponds to the second vane 6. The bush of 2 is 8. The substantially semi-cylindrical shape is configured as a pair, and the substantially semi-cylindrical bushes 7 and 8 are fitted into the bush holding portions 4d and 4e of the rotor portion 4a. The vane portion 5a of the vane 5 is held so as to be sandwiched between the pair of inserted bushes 7. Similarly, the vane portion 6a of the vane 6 is held so as to be held between the pair of inserted bushes 8. Further, the vane portion 5a is moved in the radial direction of the rotor portion 4a by moving from the bush holding portion 4d to the vane relief portion 4f. Similarly, the vane part 6a is moved in the radial direction of the rotor part 4a by moving from the bush holding part 4e to the vane relief part 4g. That is, the vanes 5a and 6a of the vanes 5 and 6 can be rotated in the circumferential direction of the rotor 4a with respect to the rotor 4a and can move substantially in the radial direction of the rotor 4a inside the bushes 7 and 8. Retained. The vane portions 5a and 6a of the vanes 5 and 6 inserted and held in the bush holding portions 4d and 4e and the vane relief portions 4f and 4g are outer peripheral surfaces of the rotor portion provided in the bush holding portions 4d and 4e of the rotor portion 4a. The vane tip portions 5d and 6d move from the 4k opening toward the cylinder inner peripheral surface 1b, and a space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k is formed in the longitudinal direction of the vane portions 5a and 6a. A plurality of working chambers or suction chambers or compression chambers are formed in the partition and cylinder;

  Next, the operation will be described. The rotating shaft portion 4b of the rotor shaft 4 receives rotational power from the driving portion of the electric element 102 or the like (engine in the case of engine driving), and the rotor portion 4a rotates in the cylinder 1. With the rotational movement of the rotor part 4a, the bush holding parts 4d and 4e arranged near the outer periphery of the rotor part 4a circulate on the circumference with the rotor shaft 4 as the central axis. A pair of bushes 7 and 8 are held by the bush holding portions 4d and 4e, respectively, and the vane portions 5a and 6a of the vanes 5 and 6 are rotatable between the bushes 7 and 8 in the circumferential direction of the rotor portion 4a. Is retained. In other words, the bush holding portions 4d and 4e and the bushes 7 and 8 form the holding portions for the vanes 5 and 6 of the rotor portion 4a, and the vanes 5 and 6 together with the holding portions for the rotor portion 4a are arranged in the circumferential direction of the rotor portion 4a. It moves and goes around the rotor shaft 4.

  On the other hand, the vane portions 5a and 6a of the vanes 5 and 6 are held by the holding portion of the rotor portion 4a so as to be movable in the almost radial direction of the rotor portion 4a. On the other hand, the vane aligner portions 5b, 5c, 6b, 6c provided in the axial direction of the vane portions 5a, 6a are rotated by the recesses 2a, 3a formed on the side of the frame 2 and the cylinder head 3 in contact with the cylinder 1. It is inserted so as to restrict the movement of the vanes 5 and 6 in the radial direction of the rotor portion 4a. When the rotor portion 4a rotates, the centrifugal force accompanying the rotation of the rotor portion 4a, the pressure difference between the vane back surface portions 5e, 6e side and the vane tip portions 5d, 6d side, specifically, the recesses 2a, 3a and the rotor portion 4a. And the pressure difference between the refrigerant entering the space formed by the cylinder and the pressure difference between the refrigerant pressure in the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k. It moves in the radial direction toward 1b. At this time, the vane aligner portions 5b, 5c, 6b, and 6c are pressed against the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a by the outer peripheral surfaces thereof, that is, the side surfaces on the vane tip portions 5d and 6d side. The amount of movement toward the inner peripheral surface 1b is limited. The vane aligners 5b, 5c, 6b, and 6c and the recesses 2a and 3a allow the vanes 5 and 6 to move toward the cylinder inner peripheral surface 1b more than necessary, without contacting the cylinder inner peripheral surface 1b. A minute gap can be formed between the portions 5d and 6d and the cylinder inner peripheral surface 1b.

Next, when the rotor portion 4a rotates, the vane aligners 5b, 5c, 6b, and 6c provided on the vanes 5 and 6 together with the vanes 5 and 6 are also pressed against the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a. To move in the circumferential direction of the recesses 2a, 3a. The vane portions 5a and 6a of the vanes 5 and 6 have a longitudinal direction that is perpendicular to the arc-shaped outer peripheral surface of the vane aligner portions 5b, 5c, 6b, and 6c, that is, a normal direction, and the vane tip portions 5d and 6d have vanes. The aligner portions 5b, 5c, 6b, and 6c are provided so as to face away from the center of the arc, that is, toward the outside. Therefore, when the vane aligner portions 5b, 5c, 6b, 6c are pressed against the inner peripheral surfaces 2d, 3d of the recesses 2a, 3a, the longitudinal direction of the vane portions 5a, 6a is the radial direction of the recesses 2a, 3a, that is, the cylinder chamber 1a. Facing the radial direction. A space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k is partitioned in the longitudinal direction of the vane portions 5a and 6a to form a compression chamber and a suction chamber.
On the other hand, since the central axis C of the rotor portion 4a and the central axis B of the cylinder chamber 1a are provided at eccentric positions, the radial direction of the rotor portion 4a and the radial direction of the cylinder chamber 1a, that is, the rotor portion outer peripheral surface 4k. The normal direction and the normal direction of the cylinder inner peripheral surface 1b are different. When the vane portions 5a and 6a move the holding portion of the rotor portion 4a to partition the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k, the longitudinal direction of the vane portions 5a and 6a is the diameter of the rotor portion 4a. The vane aligner portions 5b, 5c, 6b, 6c and the inner peripheral surfaces 2d, 3d of the recesses 2a, 3a interfere with the radial direction of the cylinder chamber 1a to be regulated. On the other hand, the bushes 7 and 8 holding the vane portions 5a and 6a in the rotor portion 4a are rotated in the bush holding portions 4d and 4e so that the longitudinal direction of the vane portions 5a and 6a is held by the rotor portion 4a. The direction is changed from the moving direction to the normal direction of the cylinder inner peripheral surface 1b. Thereby, the direction in which the vane portions 5a and 6a move the holding portion of the rotor portion 4a interferes with the longitudinal direction of the vane portions 5a and 6a that partition the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k. Things will disappear.
Thus, the vanes 5 and 6 are spaces formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k in a state where the longitudinal direction of the vane portions 5a and 6a substantially coincides with the normal direction of the cylinder inner peripheral surface 1b. And can move in the circumferential direction of the cylinder chamber 1a in the cylinder chamber 1a.

  On the other hand, in the recesses 2a and 3a, rotating shaft portions 4b and 4c are disposed at positions eccentric from the central axis B of the cylinder chamber 1a. However, since the vane aligner portions 5b, 5c, 6b, and 6c are configured to have a circular arc shape, that is, a shape having a space at the center of rotation, the vane aligner portions 5b, 5c, 6b, and 6c are connected to the rotating shaft portions 4b and 4c. It is configured to rotate around it without contact.

  In order to smoothly move the vane tip portions 5d and 6d along the cylinder inner peripheral surface 1b, the inner peripheral surfaces of the recesses 2a and 3a are formed in a cylindrical shape concentric with the cylinder inner peripheral surface 1b. The aligner portions 5b, 5c, 6b, and 6c also have an arc shape having the same diameter as the inner peripheral surfaces of the concave portions 2a and 3a, and move on the inner peripheral surfaces of the concave portions 2a and 3a, that is, on the concentric circumference of the central axis B of the cylinder chamber 1a. I can do it.

The vane aligner portions 5b, 5c, 6b, 6c are pressed against the inner peripheral surfaces of the recesses 2a, 3a and slide in the rotational direction. However, since the rotation axis parts 4b and 4c, that is, the rotation center axis C of the rotor part 4a and the center axis B of the cylinder chamber 1a are in an eccentric position, when there are a plurality of vanes, the holding part of the rotor part 4a is always The vanes face in the same direction, that is, the vanes are not held at regular intervals in the circumferential direction, and the vanes approach or distant in the circumferential direction. Therefore, for example, when there are two vanes, if the vane aligner portion is a semicircular arc of the recess, the vane aligner portions collide with each other in the circumferential direction as the rotor portion 4a rotates, and the vane portion is the cylinder inner circumferential surface. The vane tip portions 5d and 6d cannot move along the cylinder inner peripheral surface 1b without facing the normal direction of 1b. Therefore, the length in the circumferential direction is such that the vane aligner portions do not collide with each other. For example, when there are two vanes as in the present application, they are shorter than the half circumference of the inner peripheral surface of the recesses 2a and 3a. Note that how much the vane aligner portion is shortened is determined by the amount of eccentricity.
On the other hand, the vane is pressed by the inner peripheral surfaces of the recesses 2a and 3a to regulate the amount and direction of the extruded rotor portion outer surface 4k, whereas the vane aligner portions 5b, 5c, 6b and 6c If the length is too short, the force cannot be distributed over the entire vane aligner section, resulting in damage. That is, in order to disperse the pressing force on the entire vane aligner portion 5b, 5c, 6b, 6c, it is desirable to receive the force in as wide an area as possible, make the vane aligner portion as long as possible in the circumferential direction, and further the vane aligner portion. The entirety is configured to abut against the inner peripheral surfaces of the recesses 2a and 3a. As a result, while the force that the vane aligner portion presses is dispersed, the amount and direction in which the vane is pushed out are regulated, and the plurality of vanes are pushed against the inner peripheral surface of the recesses 2a and 3a and rotate without interference. Can slide in the direction. In addition, when the vane aligner portion is in wide contact with the inner peripheral surfaces of the recesses 2a and 3a, the formation of the oil film of the lubricating oil supplied thereto is also improved.
Due to the configuration of the bush holding portions 4d and 4e, the bushes 7 and 8, the vane aligner portions 5b, 5c, 6b and 6c, the concave portion 2a of the frame 2, and the concave portion 3a of the cylinder head 3, the longitudinal direction of the vane portions 5a and 6a is determined. The direction of the normal to the cylinder inner peripheral surface 1b, that is, the direction from the cylinder inner peripheral surface 1b to the direction of the central axis of the cylinder is regulated, and the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k is partitioned. The portions 5d and 6d move along the cylinder inner peripheral surface 1b without contacting the cylinder inner peripheral surface 1b while forming a minute gap of about several μm with the cylinder inner peripheral surface 1b. The minute gap is sealed with refrigeration oil supplied to the compression element 101 from the bottom of the hermetic container 103.
The inner diameters of the recesses 2a and 3a are smaller than the outer diameter of the rotor, but the inner diameter range of the recesses 2a and 3a includes the central axis of the rotor shaft 4.

  Since the rotation shafts 4b and 4c of the rotor shaft 4 are arranged on the center axis C which is eccentric from the center axis B of the cylinder chamber 1a of the cylinder 1 as shown in FIG. It arrange | positions in the cylinder chamber 1a so that it may have the closest part A to which the surface 4k and the cylinder internal peripheral surface 1b adjoin, and it rotates on the central axis C eccentric with the central axis B of the cylinder chamber 1a. In the closest portion A, a minute gap is formed between the rotor outer peripheral surface 4k and the cylinder inner peripheral surface 1b, and the rotor outer peripheral surface 4k and the cylinder inner peripheral surface 1b rotate without contact. . The minute gap is sealed with refrigeration oil supplied to the compression element 101.

FIG. 4 is a top view of the compression element 101 of the vane compressor and shows the compression operation. With reference to FIG. 4, the state in which the volume (compression chamber or suction chamber) formed by the rotor portion 4 a and the two vane portions 5 a and 6 a changes in volume in the cylinder 1 as the rotor shaft 4 rotates will be described. To do. First, in FIG. 4, the phase at which the first vane tip 5d is applied to the closest portion A between the rotor portion 4a of the rotor shaft 4 and the cylinder inner peripheral surface 1b is defined as “angle 0 °”. Then, the angles at which the rotor portion 4a rotates counterclockwise from the “angle 0 °” state are respectively “angle 0 °”, “angle 45 °”, “angle 90 °”, “angle 135 °”, “ In FIG. 4, the positions of the vanes 5 and 6 are shown as “angle 180 °”, “angle 225 °”, “angle 270 °”, and “angle 315 °”. Note that the arrow D shown in the “angle 0 °” diagram of FIG. 4 is the rotation direction of the rotor shaft 4 (counterclockwise in FIG. 4), and the other “angle 45 °” to “angle 315 °” diagrams. Then, the arrow which shows the rotation direction of the rotor shaft 4 is abbreviate | omitted. Similarly, the central axis B of the cylinder chamber 1a and the central axis C of the rotation shaft portions 4b and 4c at positions eccentric from the central axis B are also shown in the “angle 0 °” diagram, and the “angle 45 °” to “ In the figure of “angle 315 °”, the symbols are omitted.
As the rotor shaft 4 rotates, the cylinder 1 sequentially changes from the “angle 0 °” state to the “angle 315 °” state, and after the “angle 315 °” state, the “angle 0 °” again. The state returns to "". The broken arrows indicate the direction in which the vanes 5 and 6 are pushed from the rotor portion outer peripheral surface 4k toward the cylinder inner peripheral surface 1b.

  The rotor portion outer peripheral surface 4k of the rotor shaft 4 and the cylinder inner peripheral surface 1b are separated from each other by a predetermined distance in the rotation direction of the rotor portion 4a, that is, counterclockwise, from the vicinity of the closest portion A (top dead center). A suction port 1c is provided at a position (for example, a position rotated by about 45 °).

  Further, a position (for example, about a distance from the vicinity of the closest portion A where the rotor portion 4a of the rotor shaft 4 and the cylinder inner peripheral surface 1b are closest to each other in the counter-rotating direction of the rotor portion 4a, that is, the clockwise direction). A discharge flow path 1d and a discharge port 2c are provided at a position rotated by 45 °. Accordingly, the suction port 1c, the discharge flow path 1d, and the discharge port 2c are provided at a position sandwiching the closest portion A.

  In the case of “angle 0 °” and “angle 180 °” in FIG. 4, two internal spaces partitioned by the vanes 5 and 6 are formed in the cylinder 1, that is, in the cylinder chamber 1a. In the case of “angle 0 °”, the space 202 on the rotation direction side (counterclockwise direction side) of the rotor portion 4a as viewed from the left side space, that is, the closest portion A is in the middle of the suction process, and the volume increases with rotation, Low-pressure refrigerant gas is sucked from a suction port 1c formed in the cylinder 1. The space 201 on the counter-rotation direction side (clockwise direction side) of the rotor portion 4a when viewed from the right side space, that is, the closest portion A, is in the middle of the compression process, and the volume decreases with rotation, and the refrigerant gas in the space is compressed. . The space 201 communicates with the discharge port 2c, but is closed by a discharge valve (not shown) provided in the discharge port 2c, and continues to be compressed as the volume is reduced. When the pressure of the refrigerant gas in the space 201 reaches a predetermined pressure (pressure in the sealed container), the discharge valve opens, and the refrigerant gas in the space 201 is discharged from the space 201 into the sealed container 103 via the discharge port 2c. Is done. That is, it becomes a discharge process. A space in the suction process such as the space 202 is called a suction chamber, and a space in the compression process like the space 201 is called a compression chamber. Similarly, in the case of “angle 180 °”, the space 203 on the rotation direction side of the rotor portion 4a as viewed from the closest portion A is also the space on the counter rotation direction side of the rotor portion 4a as viewed from the closest portion A during the suction process. 202 is in the middle of the compression process. The discharge port 2c communicates with the space 202 but is closed by the discharge valve. When the space 202 reaches a predetermined pressure, the discharge valve opens and the operation of discharging the refrigerant gas in the space 202 is the same. is there.

  At “angle 45 °” and “angle 225 °” in FIG. 4, three spaces are formed in the cylinder 1. They will be described counterclockwise from the closest portion A (top dead center). In the case of “angle 45 °”, the space 203 from the closest part A (top dead center) to the vane 5 is a newly formed suction chamber, but is not yet communicated with the suction port 1c. Further proceeding counterclockwise, the space 202 sandwiched between the vanes 5 and 6 serves as a suction chamber communicating with the suction port 1c. A space 201 from the vane 6 to the closest portion A (top dead center) becomes a compression chamber in the middle of the compression process. Similarly, in the case of “angle 225 °”, the space 204 from the closest portion A (top dead center) to the vane 6 is a newly formed suction chamber, and the space 203 sandwiched between the vane 6 and the vane 5 is The suction chamber communicates with the suction port 1c. A space 202 from the vane 5 to the closest part A (top dead center) is a compression chamber in the middle of the compression process.

  Even at “angle 90 °” and “angle 270 °” in FIG. 4, three spaces are formed in the cylinder 1. They will be described counterclockwise from the closest portion A (top dead center). In the case of “angle 90 °”, the space 203 from the closest part A (top dead center) to the vane 5 is a suction chamber. The space 202 sandwiched between the vane 5 and the vane 6 has a maximum volume during this phase, and the suction process is completed and the suction port 1c is not communicated. Thereafter, the space 202 is changed from the suction chamber to the compression chamber, and is a compression process for compressing the refrigerant gas inside. The suction port 1c communicates with the space 203, and refrigerant gas starts to be sucked into the space 203. The space 201 from the vane 6 to the closest part A (top dead center) is compressed or the refrigerant gas in the space 201 reaches a predetermined pressure (pressure in the sealed container), and the refrigerant gas is transferred from the space 201 to the sealed container 103. It is a space that serves as a discharge process for discharging into the interior. Similarly, in the case of “angle 270 °”, the space 204 from the closest portion A (top dead center) to the vane 6 is the suction chamber, and the space 203 sandwiched between the vane 6 and the vane 5 has completed the suction process. Start the compression process. That is, the suction chamber is changed to the compression chamber, and the refrigerant gas starts to be compressed. A space 202 from the vane 5 to the closest portion A (top dead center) is a space in the compression process or the discharge process.

  Even at “angle 135 °” and “angle 315 °” in FIG. 4, three spaces are formed in the cylinder 1. They will be described counterclockwise from the closest portion A (top dead center). In the case of “angle 135 °”, the space 203 from the closest portion A (top dead center) to the vane 5 is a suction chamber. A space 202 sandwiched between the vanes 5 and 6 is in the middle of the compression process, and the inside becomes a space of intermediate pressure. A space 201 from the vane 6 to the closest portion A (top dead center) is a space in the middle of the discharge process. Similarly, in the case of “angle 315 °”, the space 204 from the closest portion A (top dead center) to the vane 6 is a suction chamber, and the space 203 sandwiched between the vane 6 and the vane 5 is in the middle of the compression process. It is space. A space 204 from the vane 5 to the closest portion A (top dead center) is a space in the middle of the discharge process.

  Through the above process, the space 201 from the vane 6 to the closest part A (top dead center) in the case of “angle 180 °” and the vane 5 from the vane 5 of “angle 0 °” to the closest part A (top dead center) The space 202 disappears.

  Thus, the rotation of the rotor shaft 4 causes the space formed in the rotation direction of the rotor portion 4a, that is, the counterclockwise direction from the closest portion A (top dead center) in the cylinder chamber 1a to communicate with the suction port 1c. The volume gradually increases with the rotation of the portion 4a, and the refrigerant is sucked from the suction port 1c. The space adjacent to the space in the rotational direction and counterclockwise direction of the rotor portion 4a with the vane interposed therebetween gradually decreases in volume, and the refrigerant therein is compressed. Then, the refrigerant compressed to a predetermined pressure is discharged from the discharge port 2 c provided in the frame 2 into the sealed container 103.

  As described above, in the compression element 101, the volume of the space between the closest part A (top dead center) and the vane or the two vanes gradually changes as the rotor part 4a rotates in the cylinder chamber 1a. Then, the refrigerant is sucked into the space from the suction port 1c, the sucked refrigerant is compressed, and the operation of being discharged from the discharge port 2c into the sealed container 103 is repeatedly performed when a predetermined pressure is reached.

  On the other hand, during one round from “angle 0 °” to “angle 315 °”, the vane aligner portions 5b, 5c, 6b, 6c are pressed against the inner peripheral surfaces 2d, 3d of the recesses 2a, 3a and the bushes 7, 8 As the vanes 5 and 6 rotate in the bush holding portions 4d and 4e, the longitudinal directions of the vane portions 5a and 6a indicated by the directions of the broken arrows substantially coincide with the normal direction of the cylinder inner peripheral surface 1b. In this state, the space formed by the cylinder inner peripheral surface 1b and the rotor portion outer peripheral surface 4k is partitioned, and the inside of the cylinder chamber 1a is moved in the circumferential direction of the cylinder chamber 1a.

  In a vane type compressor having such a configuration and operation, in order to be applied to a larger air conditioner, the volume of the compression chamber is increased without increasing the outer shape, that is, the displacement of the compression element is increased. There is a need. Further, even in a conventional air conditioner, if the displacement amount of the compression element can be increased without increasing the outer shape, the compressor can be used at a low rotation, leading to improvement in noise and efficiency. However, in the vane type compressor, when the displacement amount of the compression element is increased, there are many restrictions and cannot be easily performed.

  In the vane-type compressor, a problem and a solution when trying to increase the displacement of the compression element will be described. FIG. 5 shows the positional relationship between the vanes 5 and 6, the rotation shaft portions 4 b and 4 c of the rotor shaft 4, and the outer periphery of the rotor portion 4 a of the rotor shaft 4, and the rotation shaft portions 4 b and 4 c of the rotor shaft 4. FIG. 5 (a) is a vane type compressor as in the prior art (a configuration in which the small-diameter portions are not formed on the rotating shaft portions 4b and 4c of the rotor shaft 4). It is a top view which shows the structure of this compression element. 5 (b) and 5 (c) show a configuration and problems when the eccentric amount of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a is temporarily increased in order to increase the amount of displacement compared to FIG. 5 (a). FIG. FIG. 5D is a diagram illustrating a configuration that solves the problem when the amount of eccentricity is increased.

  In the compression element 101 of the vane type compressor, the vane aligner portions 5 b, 5 c, 6 b, 6 c are fitted in the recess 2 a of the frame 2 and the recess 3 a of the cylinder head 3 in FIG. However, if even a part of the recesses 2a and 3a is arranged in the axial direction of the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k, the space and the recesses 2a and 3a come to communicate with each other. The suction chamber and the compression chamber formed by the vanes 5 and 6 in this space are in communication with each other through the recesses 2a and 3a. As a result, compression is not possible. In order to prevent the recesses 2a and 3a from communicating with the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k, the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a rotate from the rotor outer peripheral surface 4k. It is necessary to design so as to be provided on the side of the shaft portions 4b and 4c. Accordingly, the vane aligner portions 5b, 5c, 6b, and 6c that are fitted into the recesses 2a and 3a are also disposed closer to the rotating shaft portions 4b and 4c than the rotor outer peripheral surface 4k in the axial direction of the rotating shaft.

  On the other hand, when the rotor portion 4a rotates in the cylinder chamber 1a by the rotational force of the rotating shaft portions 4b and 4c, the vanes 5 and 6 held in the rotor portion 4a also move in the cylinder chamber 1a in the rotation direction of the rotor portion 4a. That is, it moves in the circumferential direction of the cylinder chamber 1a. The vane aligners 5b, 5c, 6b and 6c provided on the vanes 5 and 6 also move in the recesses 2a and 3a along the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a as the vanes 5 and 6 move. Move in the circumferential direction. In the recesses 2a and 3a, rotary shafts 4b and 4c are arranged at positions deviated from the central axes of the recesses 2a and 3a, that is, the center axis of the cylinder chamber 1a. As the rotary shafts 4b and 4c rotate. The vane aligner portions 5b, 5c, 6b, and 6c circulate around the rotary shafts 4b and 4c. Since the rotation shafts 4b and 4c are arranged at positions eccentric with respect to the center axis of the cylinder chamber 1a, the rotor unit 4a with the center axis arranged at a position eccentric with respect to the center axis of the cylinder chamber 1a is The cylinder inner peripheral surface 1b and the rotor portion outer peripheral surface 4k have the closest portion A where the cylinder is closest. Similarly, the rotation shafts in the recesses 2a and 3a arranged at positions decentered with respect to the central axis of the recesses 2a and 3a are also the outer peripheral surfaces of the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the rotation shaft portions 4b and 4c. It has a closest portion that is closest to the face. For this reason, the vane aligner portions 5b, 5c, 6b, and 6c that circulate around the rotary shaft portions 4b and 4c provide gaps between the inner peripheral surfaces 2d and 3d of the concave portions 2a and 3a and the outer peripheral surfaces of the rotary shaft portions 4b and 4c. If the inner diameters of the recesses 2a and 3a are too small, the vane aligner portions 5b, 5c, 6b, and 6c cannot pass through the gap. Therefore, the inner diameters of the recesses 2a and 3a need to be designed to a size that allows the vane aligner portions 5b, 5c, 6b, and 6c to pass through the gap between the portions where the recesses 2a and 3a and the rotating shaft portions 4b and 4c are closest to each other. There is.

  The gap between the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the outer peripheral surfaces of the rotating shaft portions 4b and 4c is slightly wider than the radial thickness of the vane aligner portions 5b, 5c, 6b, and 6c. Although set, the thickness of the vane aligner portions 5b, 5c, 6b, 6c in the radial direction is set to a strength that does not damage the stress when the vanes 5, 6 are pressed by the differential pressure of the refrigerant. If it is a low-pressure refrigerant as in the present application, there is no problem if it is about 6 mm.

On the other hand, in the compression element that forms the suction chamber and the compression chamber by dividing the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k by the vanes 5a and 6a, in order to increase the displacement of the compression element, A design method is generally used in which the outer diameter is reduced and the amount of eccentricity of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a is increased.
However, as shown in FIG. 5B, when the outer diameter of the rotor portion 4a is reduced and the amount of eccentricity of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a is increased, the vane portion is the holding portion of the rotor portion 4a. The position of the vane portion that has moved to the maximum in the radial direction from the rotor outer peripheral surface 4k toward the cylinder inner peripheral surface 1b side, that is, the vane portion appears almost entirely in the cylinder chamber 1a from the rotor portion 4a (the angle of the vane portion is 180 °). In the position (the position of the vane portion 6a in FIG. 5B), the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a are located on the cylinder inner peripheral surface 1b side from the rotor outer peripheral surface 4k in the axial direction of the rotating shaft. 2a and 3a communicate with the space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k, and the suction chamber and the compression chamber cannot be formed.
Therefore, as shown in FIG. 5C, by reducing the inner diameters of the recesses 2a and 3a and the outer diameters of the vane aligner portions 5b, 5c, 6b and 6c from the state shown in FIG. 5B, the recesses 2a and 3a are reduced. Between the inner peripheral surface 1b of the cylinder and the outer peripheral surface 4k of the rotor portion is eliminated, but the vane portion moves the holding portion of the rotor portion 4a in the radial direction from the outer peripheral surface 4k of the rotor portion to the central axis side of the rotor portion 4a. A position where the vane portion is moved to the maximum, that is, a position where almost all the vane portion is accommodated in the rotor portion 4a (a position where the angle of the vane portion is 0 °, the position of the vane portion 5a in FIG. 5C), that is, a concave portion. 2a, 3a and the rotating shaft portions 4b, 4c are closest to each other, the trajectory of the vane aligner portions 5b, 5c, 6b, 6c intersects with the rotating shaft portions 4b, 4c, and the vane aligner portions 5b, 5c, 6b. 6c is the recess 2a, a of the inner peripheral surface 2d, 3d and the rotary shaft portion 4b, it becomes impossible to pass through the gap between the outer peripheral surface of 4c.
Therefore, in order to reduce the outer diameter of the rotor portion 4a and increase the amount of eccentricity of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a, the outer diameter of the rotor portion 4a, the inner diameter of the recesses 2a and 3a, and the rotation shaft It is necessary to adjust the amount of eccentricity, and adjustment is not easy.

As a solution for the state of FIG. 5 (c), although not shown, the entire rotating shafts 4b and 4c are reduced in diameter, and the gaps between the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the outer peripheral surfaces of the rotating shafts 4b and 4c are shown. However, when the diameter of the rotating shafts 4b and 4c is reduced without changing the material or the like, the frame 2 or the cylinder head 3 that supports the rotating shaft against the load caused by the pressure received by the rotor 4a. The bearing portions 2b and 3b and the rotating shaft portions 4b and 4c cannot have sufficient load capacity, and the bearing portions 2b and 3b and the rotating shaft portions 4b and 4c are damaged.
To reduce the load on the bearings 2b and 3b, there is a method of increasing in the axial direction, but it is necessary to increase in the height direction of the compressor, which is contrary to increasing the displacement without increasing the size of the compressor. To do.
Therefore, it is difficult to reduce the diameter of the entire rotating shaft 4b, 4c.

In view of this, in the present application, a problem is solved by providing a relief portion at a portion where the rotating shaft portions 4b and 4c of the rotor shaft 4 interfere with the vane aligner portions 5b, 5c, 6b and 6c. Here, a specific example of the escape portion will be described with an example in which the small diameter portions 4h and 4j are provided on the rotation shaft portions 4b and 4c in the recesses 2a and 3a. FIG. 5D is a diagram for explaining an example thereof. In addition, FIG.5 (d) is the same thing as the structure demonstrated in FIGS.
FIG. 5 (d) shows that the vanes 5a and 6a of the vanes 5 and 6 are rotatable in the circumferential direction of the rotor portion 4a and the rotor portion in the holding portion of the rotor portion 4a in the same manner as (a) to (c). The vane aligner portions 5b, 5c, 6b, and 6c are fitted into the recesses 2a of the frame 2 and the recesses 3a of the cylinder head 3 so that the rotor portion 4a rotates along with the rotation of the rotor portion 4a. Move in the circumferential direction. The rotor part 4a passes through the recess 2a through the bearing part 2b of the frame 2 and passes through the recess 3a through the bearing part 3b of the cylinder head 3 and the rotary shaft part 4b provided on the rotary shaft of the rotor part. And a rotating shaft portion 4c provided on the rotating shaft of the rotor portion. The vane aligner portions 5b, 5c, 6b, and 6c are arranged around the rotating shaft portions 4b and 4c along the inner peripheral surfaces of the recesses 2a and 3a. Therefore, it cannot pass through the gap between the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the outer peripheral surface of the rotary shafts 4b and 4c, and interferes with the rotary shafts 4b and 4c. The diameter of the rotating shaft portion in 3a is made smaller than the diameter of the rotating shaft portion that slides with the bearing portions 2b and 3b, whereby the outer peripheral surfaces of the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the rotating shaft portions 4b and 4c. Widen the gap between the surfaces in the radial direction. Thereby, the vane aligner portions 5b, 5c, 6b, and 6c can pass through the gap. Since the rotating shafts in the recesses 2a and 3a slide with the bearings 2b and 3b and do not support the load applied to the rotor shaft 4, there is no problem in strength even if the diameter is reduced. On the other hand, since the rotation shaft portion sliding with the bearing portions 2b and 3b and the bearing portions 2b and 3b does not change the diameter of the rotation shaft portion and the position supporting the rotor shaft 4 from the conventional one, The load does not change. Therefore, the strength remains the same as before.

The narrow diameter portions 4h, 4j provided on the rotary shaft portions 4b, 4c in the recesses 2a, 3a allow the vane aligner portions 5b, 5c, 6b, 6c to pass therethrough. Directional dimensions are almost the same.
Further, since the small diameter portions 4h and 4j are provided between the rotor portion 4a and the rotating shaft portion received by the bearings 2b and 3b, the bearing portion is a rotor in order to support the rotor portion 4a to which a load is applied from the outside. It is advantageous in terms of strength to be as close as possible to the portion 4a, and the narrow diameter portions 4h and 4j are preferably arranged as short as possible in the axial direction. Furthermore, as the diameter of the beam is reduced by reducing the diameter, the shorter the beam, the better the strength, which is convenient. Therefore, the vane aligner portion is also arranged at a position directly connected to the vane portion in the axial direction, so that the small diameter portions 4h and 4j are provided in the vicinity of the rotor portion 4a in the axial direction, and the bearing portion is as close to the rotor portion 4a as possible. Can be placed.

In such a configuration, first, by reducing the inner diameter of the recess 2a of the frame 2 and the inner diameter of the recess 3a of the cylinder head 3, a position where the vane portion appears almost entirely in the cylinder chamber 1a from within the rotor portion 4a (the vane portion is In the position at an angle of 180 ° (the position of 6a in FIG. 5 (d)), the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a are closer to the rotating shaft than the outer peripheral surface 4k of the rotor portion in the axial direction of the rotating shaft. 3a is ensured in an appropriate position so as not to communicate with the space formed by the cylinder inner peripheral surface 1b and the rotor portion outer peripheral surface 4k.
Then, with the inner diameters of the recesses 2a and 3a, the position at which the vane part is almost entirely stored in the rotor part 4a (the position of the vane part at an angle of 0 °, the position of 5a in FIG. 5D), that is, the recess 2a. 3a, the vane aligner portion is closer to the central axis side than the outer peripheral surface of the rotating shaft portions 4b and 4c in the axial direction at the closest portion where the inner peripheral surfaces 2d and 3d of the rotating shaft portions 4b and 4c are closest to each other. However, the vane aligner portion passes through the gap between the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the outer peripheral surfaces of the rotating shaft portions 4b and 4c, that is, the outer peripheral surfaces of the small diameter portions 4h and 4j, by the small diameter portions 4h and 4j. It becomes the structure which is expanded so that it can do and does not contact the rotating shaft parts 4b and 4c. That is, when the vanes 5 and 6 move in the cylinder chamber 1a in the circumferential direction in accordance with the rotational movement of the rotor portion 4a, the vane aligner provided in the vanes 5 and 6 also moves in the recesses 2a and 3a. The gap between the inner peripheral surfaces 2d and 3d of the concave portions 2a and 3a and the outer peripheral surfaces of the rotary shaft portions 4b and 4c is moved from the outer peripheral surface of the rotary shaft portions 4b and 4c. The axial side can be passed without contacting the outer peripheral surfaces of the rotating shaft portions 4b and 4c, that is, the outer peripheral surfaces of the small diameter portions 4h and 4j.
As described above, even if the inner diameter of the recess 2a of the frame 2 and the inner diameter of the recess 3a of the cylinder head 3 are reduced in order to increase the amount of eccentricity of the center axis of the rotor shaft 4 with respect to the center axis of the cylinder chamber 1a, the recesses 2a, 3a Since the inner peripheral surfaces 2d and 3d and the outer peripheral surfaces of the rotating shaft portions 4b and 4c are provided in the rotating shaft portions 4b and 4c where the outer peripheral surfaces are closest to each other, an escape portion for releasing the vane aligner portions 5b, 5c, 6b and 6c is provided. Even if the vane aligner portions 5b, 5c, 6b, and 6c circulate around the rotary shaft portions 4b and 4c, the inner peripheral surfaces 2d and 3d of the concave portions 2a and 3a and the outer peripheral surfaces of the rotary shaft portions 4b and 4c are located at the closest portions. The vanes 5 and 6 held in the rotor portion 4a can move on the circumference around the central axis of the cylinder chamber 1a by the rotational motion of the rotor portion 4a.

  With the configuration as described above, it is possible to increase the amount of eccentricity of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a, so that a compressor with a large displacement can be configured without increasing the size of the cylinder 1. Become.

For example, as shown in FIG. 6, the inner diameter of the cylinder chamber 1a is a, the outer diameter of the rotor 4a is b, the inner diameter of the recess 2a of the frame 2 and the inner diameter of the recess 3a of the cylinder head 3 are c, and the rotation shafts 4b and 4c. Where d is the outer diameter of the rotor shaft 4 and e is the outer diameter of the small diameter portions 4h and 4j of the rotor shaft 4, without changing the inner diameter of the cylinder 1, the amount of eccentricity of the central axis of the rotor shaft 4 relative to the central axis of the cylinder chamber 1a To increase the outer diameter b of the rotor portion 4a by about 95.2% before the increase in eccentricity, and the inner diameter of the recess 2a and the inner diameter c of the recess 3a by about 90.3% before the increase in eccentricity. However, the diameters 4h and 4j of the outer diameter e of about 62.5% with respect to the outer diameter d of the rotating shafts 4b and 4c are provided, and the position of the rotor shaft 4 with respect to the cylinder chamber 1a is set. Rotor outer peripheral surface 4k and silin Direction of the nearest portion A and the inner circumferential surface 1b is closest i.e. configuration by moving the eccentric direction. That is, a compressor with a large displacement can be configured without increasing the size of the cylinder.
The ratio of each part to the inner diameter a of the cylinder chamber 1a is about 84% of the outer diameter b of the rotor portion 4a and the inner diameters of the recesses 2a and 3a before the increase of the eccentricity with respect to the inner diameter a of the cylinder chamber 1a. In the case of 62%, when the amount of eccentricity is increased according to the present embodiment, the outer diameter b of the rotor portion 4a can be about 80% and the inner diameters of the recesses 2a and 3a can be about 56%. A compressor with a displacement increased by about 22% can be configured without changing the length.
The outer diameter e of the narrow diameter portions 4h and 4j depends on the strength of the material and the radial thickness of the vane aligner portion. The radial thickness of the vane aligner portion is pressed against the inner peripheral surface of the recess. The strength of the vane aligner is determined so as not to be damaged or deformed. The pressing force is due to the differential pressure between the refrigerant pressure in the cylinder chamber and the refrigerant pressure in the sealed container. When using a low-pressure refrigerant as in the present application, the vane aligner can be made as thin as possible. An increase in volume can also be expected.

  Here, the vane aligner portions 5b, 5c, 6b, and 6c have been described as examples in contact with the rotating shaft portions 4b and 4c of the recesses 2a and 3a. However, when such a configuration is performed, the vane portions 5a and 5b The one that is provided in the axial direction and moves in the circumferential direction of the rotor portion 4a together with the vane portions 5a and 5b intersects with the rotation shaft portions 4b and 4c and comes into contact with the rotation shaft portions 4b and 4c. Therefore, what the escape part provided in the rotating shaft parts 4b and 4c escapes is not limited to the vane aligner parts 5b, 5c, 6b and 6c, but what is provided in the axial direction of the vane parts 5a and 5b is the rotating shaft. This is an escape portion for preventing contact with the portions 4b and 4c.

  Further, since the diameter of the portion that is not the sliding portion with the bearing portions 2b and 3b of the rotating shaft portions 4b and 4c of the rotor shaft 4 is reduced to form the narrow diameter portions 4h and 4j, the load on the bearing portions 2b and 3b is reduced. A highly reliable compressor can be obtained without impairing the capacity.

  Further, the inner diameters of the recesses 2a and 3a formed on the end surfaces of the frame 2 and the cylinder head 3 and the outer diameters of the vane aligner portions 5b, 5c, 6b, and 6c fitted therewith are substantially equal radii. Can slide in a fluid lubrication state with sufficient refrigerating machine oil, and thus a highly efficient and highly reliable compressor with low frictional resistance and low mechanical loss can be obtained.

  Also, the vane tips 5d and 6d have a radius substantially the same as that of the cylinder inner peripheral surface 1b, thereby forming a minute gap and making no contact, and no loss due to sliding between them occurs. Moreover, since the gas leakage from the gap between the two can be minimized, a highly efficient compressor can be obtained.

  Further, since the rotor portion 4a of the rotor shaft 4 and the rotating shaft portions 4b and 4c are integrally formed, there is no need to attach an end plate, and the number of parts is reduced, and at the same time, the deterioration of the coaxial or distortion caused by the end plate attachment is reduced. There is an effect that the rotor shaft can be configured with high accuracy without causing a problem.

As described above, in the vane type compressor, it is possible to increase the displacement of the compression element without increasing the outer shape by simply changing the configuration. It can be installed and used in air conditioners. Thereby, even if the refrigerating capacity of the air conditioner is increased, an air conditioner having a large refrigerating capacity can be configured without increasing the size of the air conditioner.
In addition, conventional air conditioners can be equipped with compressors with the same size but with a large displacement of the compression element. Therefore, the compressor must be operated at a low speed to improve noise and efficiency. Can do.

In addition, although the escape part of the rotating shaft parts 4b and 4c was demonstrated by the cylindrical shape concentric with the rotating shaft parts 4b and 4c in the cross section orthogonal to the axial direction of the rotating shaft parts 4b and 4c, it is not necessarily cylindrical. There is no need. For example, the narrow diameter portion in the direction in which the vanes 5 and 6 are arranged is made thinner than the rotating shaft portions 4b and 4c, but the narrow diameter portion in the direction perpendicular to the direction in which the vanes 5 and 6 are arranged is In the cross section perpendicular to the axial direction of the rotation shaft, which has substantially the same diameter as the rotation shaft portions 4b and 4c, the center may be an ellipse concentric with the rotation shaft portions 4b and 4c. Thereby, it is not necessary to form the useless thin diameter portions 4h and 4j, and the strength at the small diameter portion of the rotor shaft 4 can be increased.
Further, in a cross section perpendicular to the axial direction of the rotation axis, a configuration in which a narrow diameter portion in a direction in which the vanes 5 and 6 are arranged is cut out instead of a circle or an ellipse may be employed. Even in this case, the rotor shaft 4 having a smaller diameter portion can be formed.

Embodiment 2. FIG.
In the first embodiment, the vanes 5 and 6 are radiated in the radial direction, that is, the rotor due to the centrifugal force accompanying the rotation of the rotor portion 4a or the pressure difference between the vane aligner portions 5b, 5c, 6b, and 6c side and the vane tip portions 5d and 6d side. A configuration in which a space formed by the cylinder inner peripheral surface 1b and the rotor outer peripheral surface 4k is partitioned from the portion outer peripheral surface 4k toward the cylinder inner peripheral surface 1b, and a suction chamber or a compression chamber is formed in the cylinder 1 Met. However, when the pressure difference between the vane aligner side and the vane tip side at the time of starting the compressor or at low rotation is small, or when liquid refrigerant enters from the suction chamber and the pressure in the compression chamber suddenly rises due to liquid compression, etc. The force that pushes the vanes 5 and 6 back toward the center of the rotor portion 4a is larger than the force that pushes the vanes 5 and 6 out of the rotor portion outer peripheral surface 4k, and the vanes 5 and 6 move toward the center of the rotor portion 4a. try to. At this time, the vane aligner portions 5b, 5c, 6b, and 6c are turned over, that is, away from the inner peripheral surface 2d of the recess 2a of the frame 2 and the inner peripheral surface 3d of the recess 3a of the cylinder head 3, and the vane aligner portions 5b, 5c, and 6b. , 6c and the roller shaft 4 are in contact with each other, and there is a problem that they are damaged or broken. Further, the vane aligner portions 5b, 5c, 6b, 6c are separated from the inner peripheral surface 2d of the recess 2a of the frame 2 and the inner peripheral surface 3d of the recess 3a of the cylinder head 3, and the vane aligner portions 5b, 5c, 6b, 6c are recessed. When sliding freely in 2a and 3a, the supply of refrigerating machine oil to the vane aligner portions 5b, 5c, 6b and 6c becomes insufficient, and the sliding vane aligner portions 5b, 5c, 6b and 6c, and the recesses 2a and 3a The rotor portion 4a is worn or damaged. Therefore, in order to prevent the vane aligner portions 5b, 5c, 6b, 6c from separating from the inner peripheral surface 2d of the recess 2a and the inner peripheral surface 3d of the recess 3a, the inner surfaces 2d, 3d of the recesses 2a, 3a On the other hand, stoppers that restrict the movement of the vanes 5 and 6 in the radial direction are provided on the vane aligner portions 5b, 5c, 6b, and 6c. The present invention will be described in Embodiment 2.

  FIG. 7 is a longitudinal sectional view of the vane type compressor showing the second embodiment, and FIG. 8 is a perspective view of the vanes 5 and 6 provided with the stoppers of FIG. Since the vanes 5 and 6 are parts having the same shape, in FIG. 8, the vanes 5 and 6 are indicated by the reference numerals of the vanes 5. Parts having the same reference numerals as those in the first embodiment are parts that are the same as or similar to those in the first embodiment and that perform the same functions.

  The frame 2 is provided with a substantially cylindrical recess 2a that is concentric with the central axis of the cylinder chamber 1a and has an inner diameter smaller than the inner diameter of the cylinder chamber 1a on the end surface of the cylinder 1 and is fitted with vane aligner portions 5b and 6b. Yes. Similarly, the cylinder head 3 is also provided with a cylindrical recess 3a concentric with the center axis of the cylinder 1 and having an inner diameter smaller than the inner diameter of the cylinder chamber 1a on the cylinder 1 side end surface, and the vane aligner portions 5c and 6c are fitted therein. Has been.

  In addition, as for the recessed parts 2a and 3a, one side of the axial direction opens to the cylinder chamber 1a side, and the other is obstruct | occluded by the plane. That is, the recesses 2a and 3a are constituted by cylindrical side surfaces, that is, inner peripheral surfaces 2d and 3d, and circular flat surfaces 2e and 3e that close one of the axial directions. The flat surfaces 2e and 3e are provided with ring-shaped grooves 2f and 3f along the inner peripheral surfaces 2d and 3d.

  On the other hand, the vanes 5 and 6 are composed of vane portions 5a and 6a and vane aligner portions 5b, 5c, 6b, and 6c. The substantially quadrangular vane portion 5a includes a vane tip portion 5d on the cylinder inner peripheral surface 1b side, a vane back surface portion 5e on the opposite side of the rotor portion 4a, an axial direction of the rotor portion 4a, the frame 2 The side portion 5f on the side, the axial direction of the rotor portion 4a, the side portion 5g on the cylinder head 3 side, and the side portions 5h and 5j in the circumferential direction of the rotor portion 4a are configured. A vane aligner portion 5b is provided on the vane back surface portion 5e side of the side surface portion 5f in the axial direction of the vane portion 5a. Further, the vane aligner portion 5b is formed on the frame 2 side, that is, on the side opposite to the vane portion 5a, is thinner in the radial direction than the vane aligner portion 5b and is substantially concentric with the vane aligner portion 5b and extends in the axial direction. A partial ring shape, that is, an arc-shaped stopper portion 5k is provided. Similarly, a vane aligner portion 5c is provided on the vane back surface portion 5e side of the side surface portion 5g in the axial direction of the vane portion 5a, and the vane aligner portion 5c has a vane aligner on the cylinder head 3 side, that is, on the opposite side of the vane portion 5a. The stopper 5p is provided with a partial ring shape, that is, an arcuate shape, which is thinner in the radial direction than the portion 5c, is substantially concentric with the vane aligner portion 5c, and extends in the axial direction. The stopper portions 5k and 5p are provided on the outer peripheral side of the vane aligner portions 5b and 5c, that is, on the vane tip portion 5d side in order to prevent interference with the rotating shaft portions 4b and 4c.

  Similarly, the vane portion 6a includes a vane tip portion 6d on the cylinder inner peripheral surface 1b side, a vane back surface portion 6e on the side of the central axis of the rotor portion 4a on the opposite side, the axial direction of the rotor portion 4a, and the frame 2 side. Side surface portion 6f, the axial direction of the rotor portion 4a, the side surface portion 6g on the cylinder head 3 side, and the side surface portions 6h and 6j in the circumferential direction of the rotor portion 4a. A vane aligner portion 6b is provided on the vane back surface portion 6e side of the frame 2 side surface portion 6f of the vane portion 6a, and the vane aligner portion 6b is provided on the vane aligner portion 6b on the frame 2 side, that is, on the opposite side to the vane portion 5a. Also, the stopper portion 6k is provided with a partial ring shape that is thin in the radial direction, is substantially concentric with the vane aligner portion 6b, and extends in the axial direction. Similarly, a vane aligner portion 6c is provided on the vane back surface portion 6e side of the side surface portion 6g on the cylinder head 3 side of the vane portion 6a, and the vane aligner portion 6c has a vane on the cylinder head 3 side, that is, on the opposite side to the vane portion 6a. A partial ring-shaped stopper portion 6p is provided which is thinner in the radial direction than the aligner portion 6c, is substantially concentric with the vane aligner portion 6c, and extends in the axial direction. The stopper portions 6k and 6p are provided on the outer peripheral side of the vane aligner portions 6b and 6c, that is, on the vane tip portion 6d side in order to prevent interference with the rotating shaft portions 4b and 4c.

The stopper portions 5k, 5p, 6k, 6p provided on the vane aligner portions 5b, 5c, 6b, 6c are fitted into the ring-shaped grooves 2f, 3f of the recesses 2a, 3a to constitute the compression element 101. Thereby, the movement of the vanes 5 and 6 in the radial direction is restricted.
The ring-shaped grooves 2f and 3f and the stopper portions 5k, 5p, 6k, and 6p are located on the outer peripheral side of the rotating shaft portions 4b and 4c in the axial direction. When trying to increase the amount of eccentricity as much as possible, the vane aligner portions 5b, 5c, 6b, 6c are pushed into the narrow diameter portions 4h, 4j as close as possible to the nearest portion, so that the vane 5, In order to prevent interference between the stopper portions 5k, 5p, 6k, 6p and the rotating shaft portions 4b, 4c when the 6 moves, the stopper portions 5k, 5p, 6k, 6p are vane aligner portions 5b, 5c, 6b, 6c. It is made thinner in the radial direction, and is provided on the outer peripheral side of the vane aligner portions 5b, 5c, 6b, 6c, that is, on the vane tip portions 5d, 6d side.

In addition, although the stopper part provided in the vane aligner part was provided with the part on both sides of the frame side and the cylinder head side, only one of them may be provided.
Further, the stopper portion is provided on the outer peripheral side of the vane aligner portion, that is, on the vane tip portion side. However, as shown in FIGS. 7 and 8, the stopper portion and the outer peripheral surface of the vane aligner portion are not continuously connected. Also good. That is, the stopper portion may be provided slightly on the inner peripheral side from the outer peripheral side of the vane aligner portion, for example, on the inner peripheral side about the thickness of the stopper portion.
Further, the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a and the side surfaces of the ring-shaped grooves 2f and 3f may not be continuously connected. That is, the side surfaces of the ring-shaped grooves 2f and 3f may be provided slightly on the inner peripheral side of the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a, for example, on the inner peripheral side about the thickness of the stopper portion.
The width of the ring-shaped grooves 2f and 3f may be wider than the thickness of the stopper portions 5k, 5p, 6k, and 6p. For example, the thickness of the stopper portion and the width of the ring-shaped grooves 2f and 3f may be wide. Although the vanes 5 and 6 are allowed to move in the radial direction, the vane aligner portions 5b, 5c, 6b, and 6c are not overturned by such movement in the radial direction.

  Next, the operation will be described. The rotor shaft 4 receives rotational power from the drive unit, and the rotor unit 4a rotates in the cylinder 1, and the vane held between the bushes 7 and 8 of the bush holding units 4d and 4e of the rotor unit 4a with the rotation. 5 and 6 also move on the circumference with the cylinder chamber 1a as the central axis.

  The vanes 5 and 6 are separated from each other in the radial direction, that is, from the outer peripheral surface 4k of the rotor portion, due to the centrifugal force accompanying the rotation of the rotor portion 4a and the pressure difference between the vane aligner portions 5b, 5c, 6b and 6c side A force for pushing toward the cylinder inner peripheral surface 1b is received. The high pressure refrigerant in the hermetic container 103 enters the space formed by the recesses 2a and 3a on the vane aligner side and the rotor 4a from the gaps between the bearings 2b and 3b, and the rotor portion on the vane tip 5d and 6d side. Since the space between the outer peripheral surface 4k and the cylinder inner peripheral surface 1b sucks the low-pressure refrigerant, the pressure difference between the vane aligner portions 5b, 5c, 6b, 6c side and the vane tip portions 5d, 6d side is the vanes 5, 6 Is pushed out from the rotor outer peripheral surface 4k. By these forces, the vanes 5 and 6 are pushed out in the radial direction, that is, the rotor portion outer peripheral surface 4k toward the cylinder inner peripheral surface 1b. At this time, the vane aligner portions 5b, 5c, 6b, and 6c That is, the side surface opposite to the rotor shaft 4 is pressed against the inner peripheral surfaces 2d and 3d of the recesses 2a and 3a, and beyond that state, the vanes 5 and 6 are directed from the rotor outer peripheral surface 4k to the cylinder inner peripheral surface 1b in the radial direction. To prevent it from being pushed out.

  On the other hand, when the compressor is started or when the rotation is low, the centrifugal force accompanying the rotation of the rotor portion 4a is weak and the pressure in the hermetic container is not so high. Therefore, it is formed by the recesses 2a and 3a on the vane aligner side and the rotor 4a. And the pressure difference between the space between the rotor outer peripheral surface 4k on the vane tip 5d and 6d side and the cylinder inner peripheral surface 1b is small. Further, when liquid refrigerant enters from the suction chamber, the pressure in the compression chamber rapidly increases due to liquid compression. In such a case, the force that pushes the vanes 5 and 6 back toward the center of the rotor portion 4a is larger than the force that pushes the vanes 5 and 6 out of the rotor portion outer peripheral surface 4k. Try to move in the direction. In this state, the vane aligner portions 5b, 5c, 6b, and 6c are overturned and the vanes 5 and 6 are damaged. However, the ring-shaped grooves 2f and 3f of the recesses 2a and 3a and the stopper portions 5k, 5p, and 6k provided in the vane aligner portion. , 6p, the movement of the vanes 5, 6 in the central direction of the rotor portion 4a is restricted. That is, even if a force that pushes the vanes 5 and 6 back toward the center of the rotor portion 4a is applied, the vanes 5 and 6 are pushed back toward the center by the ring-shaped grooves 2f and 3f and the stopper portions 5k, 5p, 6k, and 6p. There is no overthrow. On the other hand, the sliding of the vanes 5 and 6 in the rotational direction of the rotor portion 4a is the same as the conventional one, and the compression operation does not change.

  Further, the ring-shaped grooves 2f and 3f and the stopper portions 5k, 5p, 6k, and 6p are positioned on the outer peripheral side of the rotary shaft portions 4b and 4c in the axial direction, but from the vane aligner portions 5b, 5c, 6b, and 6c. It has a thin shape in the radial direction and is provided on the outer peripheral side of the vane aligner portions 5b, 5c, 6b, 6c, that is, on the vane tip portions 5d, 6d side, thereby preventing interference with the rotating shaft portions 4b, 4c. The eccentric amount of the central axis of the rotor shaft 4 with respect to the central axis of the cylinder chamber 1a can be easily increased.

  As described above, the ring-shaped grooves 2f and 3f of the recesses 2a and 3a of the frame 2 and the cylinder head 3 and the stopper portions 5k, 5p, 6k and 6p of the vane aligner portions 5b, 5c, 6b and 6c are fitted to each other. Since the radial movements of 5 and 6 are restricted, the vanes 5 and 6 are rotors in a transient operation state such as when the compressor is started or when the rotation is low, or when liquid refrigerant enters from the suction chamber. Even if the force pushed out from the outer peripheral surface 4k toward the cylinder inner peripheral surface 1b decreases, the vanes 5 and 6 roll over, and the vane aligner portions 5b, 5c, 6b, and 6c come into contact with the rotor shaft 4, and the vane aligner The parts 5b, 5c, 6b, 6c and the rotor shaft 4 can be prevented from being damaged or broken.

  Further, the vanes 5 and 6 can be prevented from overturning, that is, the vane aligner portions 5b, 5c, 6b and 6c can be separated from the inner peripheral surface 2d of the recess 2a and the inner peripheral surface 3d of the recess 3a. It is possible to obtain a highly efficient and reliable compressor that can slide in the retained fluid lubrication state, has low frictional resistance, and has little mechanical loss.

As described above, it is possible to obtain a highly reliable compressor in which the vane does not capsize even if the operation ratio and the start-up frequency increase by increasing the displacement amount of the compression element and keeping the rotation speed of the compressor low. It is possible to improve the noise and efficiency of the air conditioner.
Further, even when liquid refrigerant enters from the suction chamber, the vane does not capsize, so that a more reliable compressor can be obtained.

  1 cylinder, 1a cylinder chamber, 1b cylinder inner peripheral surface, 1c suction port, 1d discharge flow path, 2 frame, 2a recess, 2b bearing portion, 2c discharge port, 2d inner peripheral surface, 2e circular plane, 2f ring groove, 3 cylinder head, 3a recess, 3b bearing part, 3d inner peripheral surface, 3e circular plane, 3f ring-shaped groove, 4 rotor shaft, 4a rotor part, 4b rotating shaft part, 4c rotating shaft part, 4d bush holding part, 4e bushing Holding part, 4f vane relief part, 4g vane relief part, 4h narrow diameter part, 4j narrow diameter part, 4k rotor part outer peripheral surface, 5 first vane, 5a vane part, 5b vane aligner part, 5c vane aligner part, 5d Vane tip portion, 5e Vane back surface portion, 5f side surface portion, 5g side surface portion, 5h side surface portion, 5j side surface portion, 6 second vane, 6 Vane part, 6b Vane aligner part, 6c Vane aligner part, 6d Vane tip part, 6e Vane back face part, 6f Side face part, 6g Side face part, 6h Side face part, 6j Side face part, 7 bush, 8 bush, 11 Stator, 12 Rotor, 13 Glass terminal, 14 Discharge pipe, 15 Lead wire, 100 Compressor, 101 Compression element, 102 Electric element, 103 Airtight container.

Claims (6)

A cylinder that is substantially cylindrical and open at both ends in the axial direction, a cylinder head that closes one opening of the cylinder, a frame that closes the other opening of the cylinder, and the cylinder within the cylinder A rotor shaft having a cylindrical rotor portion that rotates about a central axis that is eccentric with respect to the central axis of the rotor, and a rotary shaft portion that is provided on the central axis of the rotor portion and transmits a rotational force to the rotor portion; And is arranged in the rotor portion so that its longitudinal direction is substantially the radial direction of the rotor portion, and is rotatable in the circumferential direction of the rotor portion and movable in the radial direction of the rotor portion. Vane type compression that forms a compression chamber by partitioning a space formed by the vane held by the rotor portion and the outer peripheral surface of the rotor portion and the inner peripheral surface of the cylinder by the vane. In,
The vane includes a vane aligner that restricts the longitudinal direction of the vane and the normal direction of the inner peripheral surface of the cylinder to substantially coincide with each other and rotates around the rotating shaft portion by the rotational movement of the rotor portion,
A vane type compressor characterized in that a relief portion is provided on the rotating shaft portion so that the vane aligner and the rotating shaft portion do not contact each other. The cylinder head and the frame have a concave portion concentric with the inner diameter of the cylinder on the cylinder end surface side, and the vane aligner has a ring-shaped or arc-shaped outer shape substantially the same as the inner diameter of the concave portion, and the vane aligner The vane type compressor according to claim 1, wherein the vane aligner is held by the cylinder head or the frame by being fitted into the recess. The vane type compressor according to claim 1 or 2, wherein the relief portion is configured by a thin portion having a small diameter provided on the rotating shaft. The concave portion of the cylinder head is configured by a substantially cylindrical inner peripheral surface and an axial plane, and a ring-shaped groove is provided on the plane along the inner peripheral surface, and is fitted into the concave portion of the cylinder head. The vane compressor according to claim 2, wherein the vane aligner is provided with a locking portion that fits into the ring-shaped groove. The recess of the frame is configured by a substantially cylindrical inner peripheral surface and an axial plane, and a ring-shaped groove is provided on the plane along the inner peripheral surface, and the recess is inserted into the recess of the frame. The vane type compressor according to claim 2 or 4, wherein the vane aligner is provided with a locking portion that fits into the ring-shaped groove. The vane type compressor according to any one of claims 1 to 4, wherein a refrigerant having a normal boiling point of -45 ° C or higher is used as the refrigerant.

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