WO2015049905A1

WO2015049905A1 - Vane-type compressor

Info

Publication number: WO2015049905A1
Application number: PCT/JP2014/066914
Authority: WO
Inventors: 雷人河村; 関屋　慎; 若本　慎一; 英明前山
Original assignee: 三菱電機株式会社
Priority date: 2013-10-01
Filing date: 2014-06-25
Publication date: 2015-04-09
Also published as: JP2016205132A

Abstract

In the present invention, a vane-type compressor comprises the following: a cylinder (1) that has a cylindrical shape and both axial-direction-ends of which are open; a cylinder head (3) and a frame (2) that close both axial direction ends of the cylinder (1); shaft parts (4a, 4b) the rotational centers of which coincide with the center of the inner circumferential surface (1a) of the cylinder (1) and that rotate inside of the cylinder (1); a vane part (4c) that integrally rotates with the shaft parts (4a, 4b); a rotor (6) the rotational center of which deviates from the center of the inner circumferential surface of the cylinder (1), that is inserted at the periphery of the shaft parts (4a, 4b) via a space, and that rotates inside the cylinder (1); and a bushing (8) that is provided to the rotor (6) and that supports the vane part (4c) so that the vane part is freely rotatable with respect to the rotor (6) and movable in the radial direction of the cylinder (1). The vane part (4c) extends from the shaft parts (4a, 4b), through the bushing (8), and towards the inner circumferential surface of the cylinder (1). The rotor (6) receives transmission of the rotational force of the shaft parts (4a, 4b) via the vane part (4c) and the bushing (8) and is thereby rotated.

Description

Vane type compressor

The present invention relates to a vane type compressor.

Conventionally, “a substantially cylindrical cylinder having both ends opened in the axial direction, a cylinder head and a frame closing both ends of the cylinder, a columnar rotor portion that rotates in the cylinder, and the rotor portion” In the vane type compressor having a rotor shaft having a shaft portion for transmitting a rotational force to the rotor and a plurality of vanes installed in the rotor portion and having tip portions formed in an arc shape on the outside, the tips of the plurality of vanes The plurality of vanes are always in the normal direction of the inner peripheral surface of the cylinder so that the compression operation is performed in a state where the arc-shaped normal line of the portion and the normal line of the inner peripheral surface of the cylinder are always substantially coincident with each other Or the cylinder is held so as to have a constant inclination with respect to the normal direction of the inner peripheral surface of the cylinder, and the plurality of vanes in the rotor portion are rotatable and movable with respect to the rotor portion. A rotation support portion formed of a recess or a ring-shaped groove concentric with the cylinder inner diameter is formed on the cylinder side end surface of the cylinder head and the frame, and a part of the rotation support portion is formed in the rotation support portion. A vane type compressor in which a pair of vane aligner portions having plate-like protrusions or grooves are fitted on ring-shaped end faces, and the plate-like protrusions or grooves are fitted into grooves or protrusions provided in the plurality of vanes. Yes (see, for example, Patent Document 1).

In Patent Document 1, the vane is supported by the rotor so as to be rotatable around the center of the inner peripheral surface of the cylinder and to be movable in the radial direction of the cylinder. The compression operation is performed so that the normal of the surface is always almost the same. Thereby, the sliding state of the vane tip portion is improved, and the vane tip portion and the cylinder inner peripheral surface can operate without contact. Thus, since the vane tip and the cylinder inner peripheral surface operate in a non-contact manner, a high-performance compressor that does not generate a sliding loss at the vane tip can be realized.

A general vane compressor including the configuration of Patent Document 1 is arranged such that a part of the outer peripheral surface of the rotor portion is close to the inner peripheral surface of the cylinder via a minute gap, and the rotation center of the rotor shaft and the inner portion of the cylinder are arranged. In this arrangement, the center of the peripheral surface is eccentric.

International Publication No. 2012/023426 (Pages 6-8, Figure 2)

The vane type compressor as shown in Patent Document 1 has high performance in terms of not causing a sliding loss at the vane tip. However, since the rotation center of the shaft and the center of the cylinder inner peripheral surface are arranged eccentrically, there are the following problems. That is, considering the shaft rotation center as a reference, the cylinder radial direction thickness (hereinafter referred to as cylinder wall thickness) opposite to the eccentric side of the cylinder inner peripheral surface is smaller than the eccentric side of the cylinder inner peripheral surface. It becomes thicker, and the cylinder wall thickness can be biased in the circumferential direction.

And the cylinder wall thickness required for a certain cylinder volume is determined to some extent from the viewpoint of strength. For this reason, the cylinder thickness on the side opposite to the eccentric side of the cylinder inner peripheral surface may be set to the fixed thickness, but the cylinder thickness on the eccentric side of the cylinder inner peripheral surface is equal to the eccentric thickness. Only thicker. In other words, if the shaft rotation center (motor rotation center) and the center of the cylinder inner peripheral surface are arranged eccentrically, the cylinder outer diameter will be increased, and the cylinder outer periphery will be sealed by the increased diameter. The container also has a problem of increasing the diameter.

The present invention has been made in order to solve the above-described problems. The vane is capable of ensuring high performance by making the vane tip portion non-contact with the inner circumferential surface of the cylinder and reducing the size of the sealed container. A mold compressor is provided.

The vane type compressor according to the present invention is a cylinder having a cylindrical opening at both ends in the axial direction, a cylinder head and a frame closing the both ends in the axial direction of the cylinder, and an inner peripheral surface of the cylinder 1 at the center of rotation. The shaft part that rotates in the cylinder in line with the center of the cylinder, the vane part that rotates integrally with the shaft part, the center of rotation is eccentric from the center of the inner peripheral surface of the cylinder, and there is a space around the shaft part. A rotor that is inserted through the cylinder and rotates in the cylinder, and a bush that is installed in the rotor and supports the vane part so as to be rotatable with respect to the rotor and movable in the radial direction of the cylinder. The rotor extends from the shaft portion through the bush toward the inner peripheral surface of the cylinder, and the rotor rotates when the rotational force of the shaft portion is transmitted through the vane portion and the bush.

According to the present invention, it is possible to obtain a high-efficiency vane-type compressor capable of ensuring high performance by making the vane tip portion non-contact with the inner peripheral surface of the cylinder and miniaturizing the sealed container.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Embodiment 1 of this invention, and is a longitudinal cross-sectional view of the vane type compressor 200. FIG. FIG. 2 is a diagram illustrating the first embodiment of the present invention, and is an exploded perspective view of a compression element 101 of a vane compressor 200. FIG. It is a figure which shows Embodiment 1 of this invention, and is a figure which shows arrangement | positioning of the vane shaft 4 and the independent vane 5. FIG. FIG. 6 shows the first embodiment of the present invention, and is a cross-sectional view taken along the line II of FIG. 1 in a state where the rotation angle is 90 ° in FIG. FIG. 2 shows the first embodiment of the present invention, and is a cross-sectional view taken along the line II of FIG. 1 showing the compression operation of the vane type compressor 200. FIG. FIG. 5 is a diagram showing the first embodiment of the present invention, and is a cross-sectional view of a main part around a vane portion 4c in FIG. It is a figure which shows Embodiment 2 of this invention, and is an exploded perspective view of the compression element 101 of the vane type compressor 200. FIG. It is a figure which shows Embodiment 3 of this invention, and is sectional drawing in the state of 90 degrees of rotation angles. It is a figure which shows Embodiment 3 of this invention, (a) is a top view of the independent vane 5, (b) is a front view of the independent vane 5. FIG. FIG. 6 is a view showing a modification of the vane type compressor 200 according to Embodiments 1 to 3 of the present invention, and is a view showing the arrangement of the vane shaft 4 and the independent vanes 5. FIG. 7 is a diagram showing a modification of the vane compressor 200 according to Embodiments 1 to 3 of the present invention, and shows the modification of the vane compressor at the same position as the line II in FIG. 1 at a rotation angle of 90 °. It is sectional drawing cut | disconnected by the line | wire.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a vane type compressor 200 showing Embodiment 1 of the present invention. In FIG. 1, an arrow indicated by a solid line indicates a flow of gas (refrigerant), and an arrow indicated by a broken line indicates a flow of refrigerating machine oil 25. FIG. 2 is a diagram showing the first embodiment of the present invention, and is an exploded perspective view of the compression element 101 of the vane type compressor 200. FIG. 3 is a diagram illustrating the first embodiment of the present invention, and is a diagram illustrating the arrangement of the vane shaft 4 and the independent vanes 5. 3A is a front view of the vane shaft 4 and the independent vane 5, FIG. 3B is a cross-sectional view taken along the line II in FIG. 3A, and FIG. 3C is a cross-sectional view taken along the line II- in FIG. It is II sectional drawing. 4 is a diagram showing the first embodiment of the present invention, and is a cross-sectional view taken along the line II of FIG. 1 in a state where the rotation angle is 90 ° in FIG. 5 described later. The vane type compressor 200 will be described with reference to FIGS. In FIG. 1 to FIG. 4 and the drawings to be described later, the same reference numerals are the same or equivalent, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.

The vane compressor 200 includes a hermetic container 103, a compression element 101 housed in the hermetic container 103, an electric element 102 that is positioned above the compression element 101 and drives the compression element 101, and a bottom portion in the hermetic container 103. And an oil sump 104 for storing the refrigerating machine oil 25.

The electric element 102 that drives the compression element 101 is constituted by, for example, a brushless DC motor. The electric element 102 includes a stator 21 that is fixed to the inner periphery of the hermetic container 103, and a rotor 22 that is disposed inside the stator 21 and uses a permanent magnet. Electric power is supplied to the stator 21 from a glass terminal 23 fixed to the upper surface of the sealed container 103 by welding. A suction pipe 26 is attached to the side surface of the sealed container 103, and a discharge pipe 24 is attached to the upper surface.

As shown in FIGS. 1 and 2, the compression element 101 includes the following elements. In the present embodiment, the case where the number of vanes is two is shown.
(1) Cylinder 1: The cylinder 1 has a substantially cylindrical shape as a whole, and both ends in the axial direction are open. Further, a notch portion 1h penetrating in the axial direction and curled outward is provided in a part of the cylinder inner peripheral surface 1a, and a suction port 1c communicating with the suction pipe 26 is opened in the notch portion 1h. Further, a discharge communication channel 1d communicating with a discharge port 2d of the frame 2 described later is provided on the inner peripheral surface 1a opposite to the suction port 1c with a nearest contact point 32 (shown in FIG. 4) described later interposed therebetween. Yes. Further, an oil return hole 1e penetrating in the axial direction is provided in the outer peripheral portion of the cylinder 1.

(2) Frame 2: The frame 2 has a substantially T-shaped cross section, and the portion in contact with the cylinder 1 has a substantially disk shape, and closes one opening (upper side in FIG. 2) of the cylinder 1. A recess 2a (shown in FIG. 1) is formed on the end face of the frame 2 on the cylinder 1 side. The recess 2a is formed of an eccentric circle whose inner peripheral surface is eccentric with respect to the cylinder inner peripheral surface 1a. A rotor aligner portion 6c of the first rotor 6A, which will be described later, and a rotor aligner portion 7c of the second rotor 7A are slidably fitted in the recess 2a in the circumferential direction, and the

rotor aligner portions

6c, 7c It is supported by a rotor aligner bearing portion 2b (shown in FIG. 1) which is an inner peripheral surface. The central portion of the frame 2 is a cylindrical hollow, and a main bearing portion 2c is provided here. The concave portion 2a may be a ring-shaped concave portion in plan view or a cylindrical concave portion. In any case, the inner peripheral surface on the radially outer side of the recess 2a is formed by an eccentric circle that is eccentric with respect to the cylinder inner peripheral surface 1a.

The frame 2 is provided with a discharge port 2d at a position communicating with the discharge communication channel 1d of the cylinder 1, and the outlet of the discharge port 2d regulates the opening of a discharge valve (not shown) and the discharge valve 2e. A first discharge valve presser (not shown) is attached.

(3) Cylinder head 3: The cylinder head 3 has a substantially T-shaped cross section, and the portion in contact with the cylinder 1 has a substantially disk shape. The other opening of the cylinder 1 (the lower side in FIGS. 1 and 2) Block. A concave portion 3 a is formed on the cylinder 1 side end surface of the cylinder head 3. Although FIG. 2 shows an example in which the recess 3a is a ring-shaped recess in plan view, it may be a cylindrical recess. And the inner peripheral surface 3b on the radially outer side of the recess 3a is formed of an eccentric circle eccentric with respect to the cylinder inner peripheral surface 1a. A rotor aligner portion 6d of the first rotor 6A, which will be described later, and a rotor aligner portion 7d of the second rotor 7A, which will be described later, are slidably fitted in the recess 3a, and the

rotor aligner portions

6d, 7d It is supported by a rotor aligner bearing portion 3b which is an inner peripheral surface 3b on the radially outer side. Moreover, the center part of the cylinder head 3 is a cylindrical hollow, and the main bearing part 3c is provided here.

(4) Vane shaft 4: The vane shaft 4 has a structure in which the shaft portion 4ab and the vane portion 4c provided on the outer peripheral surface of the shaft portion 4ab are integrated. The rotation center 4i of the shaft portion 4ab coincides with the center 1f of the cylinder inner peripheral surface 1a, and the rotation of the shaft portion 4ab causes the vane portion 4c to rotate integrally with the shaft portion 4ab. Hereinafter, in the shaft portion 4ab, the upper side of the vane portion 4c may be referred to as the upper shaft portion 4a, and the lower side may be referred to as the lower shaft portion 4b. In the vane shaft 4, the upper shaft portion 4a and the lower shaft portion 4b are supported by the main bearing portion 2c of the frame 2 and the main bearing portion 3c of the cylinder head 3, respectively. The vane portion 4c is formed of a substantially square plate-like member, and the vane tip portion 4d located on the cylinder inner peripheral surface 1a side is formed in an arc shape on the outer side, and the radius of the arc shape is the cylinder inner peripheral surface. It is comprised by the radius substantially equivalent to the radius of 1a.

Further, an oil pump 31 (shown in FIG. 1) using the centrifugal force of the vane shaft 4 as described in, for example, Japanese Patent Application Laid-Open No. 2009-264175 is provided at the lower end portion of the vane shaft 4. The oil pump 31 is provided in the axial center portion of the vane shaft 4 and communicates with an oil supply passage 4e extending in the axial direction. An oil supply passage 4g is provided between the oil supply passage 4e and the recess 2a, and the oil supply passage 4e. An oil supply passage 4f is provided between the first and second recesses 3a. An oil drain hole 4h (shown in FIG. 1) is provided at a position above the main bearing portion 2c of the shaft portion 4ab.

(5) Independent vane 5: The independent vane 5 includes a vane portion 5a formed of a substantially rectangular plate-shaped member, and a rotation center 5c of the vane portion 5a (the same as the rotation center 4i of the shaft portion 4ab) (see FIG. 3). It is comprised from the hollow column-shaped rotation support part 5d provided in the end surface of illustration side, and rotates concentrically with the vane part 4c. The lower shaft portion 4b is rotatably inserted into the rotation support portion 5d. In the vane portion 5a, a vane tip portion 5b located on the cylinder inner peripheral surface 1a side is formed in an arc shape on the outer side, and the radius of the arc shape is configured to be substantially equal to the radius of the cylinder inner peripheral surface 1a. Yes. Here, the vane length direction of the vane portion 5 a and the normal direction of the arc shape of the vane tip portion 5 b are formed so as to pass through the center of the shaft portion 4 ab of the vane shaft 4.

(6) The rotor 6 is formed in an annular shape as a whole, and rotates eccentrically from the center 1f of the inner peripheral surface 1a of the cylinder 1 around its center axis (rotation center 6i (shown in FIG. 4)). As described above, the posture is controlled by the posture control means. The posture control means corresponds to

rotor aligners

6c, 7c, 6d, 7d and recesses 2a, 3a, which will be described later. The rotor 6 includes a first rotor 6A and a second rotor 7A each having a shape in which an annular ring is halved in the axial direction.

(6.1) First rotor 6A: The first rotor 6A includes a rotor portion 6j having a substantially arc shape in a plan view located in the cylinder 1, a rotor aligner portion 6c fitted into the recess 2a of the frame 2, And a rotor aligner portion 6d fitted into the recess 3a of the cylinder head 3. The outer peripheral surface of the rotor portion 6j and the outer peripheral surfaces of the

rotor aligner portions

6c and 6d are formed by the same outer peripheral surface 6a. Further, the entire circumferential end faces 6e and 6f of the first rotor 6A are partially cylindrical surface bush holding surfaces, and

bush holding portions

8A and 8B (with a bush holding surface of the second rotor 7A described later). 2 (b)).

(6.2) Second rotor 7A: The second rotor 7A includes a rotor portion 7j having a substantially arc shape in a plan view located in the cylinder 1, a rotor aligner portion 7c fitted into the recess 2a of the frame 2, And a rotor aligner portion 7d fitted into the recess 3a of the cylinder head 3. The outer peripheral surface of the rotor portion 7j and the outer peripheral surfaces of the

rotor aligner portions

7c and 7d are formed by the same outer peripheral surface 7a. Further, the entire

circumferential end surfaces

7e and 7f of the second rotor 7A are arc-shaped bush holding surfaces, and the

bush holding portions

8A and 8B (FIG. 2) together with the bush holding surface of the first rotor 6A. (Illustrated in (b)). Also, the bush holding portion 8A and the bush holding portion 8B are disposed at substantially symmetrical positions with the shaft portion 4ab interposed therebetween. The bush holding portion 8A and the

vane relief surfaces

6g and 7g communicate with each other, and the bush holding portion 8B and the

vane relief surfaces

6h and 7h communicate with each other.

(7) Bush 8: The bush holding portion 8A includes two spaced apart partial cylindrical surfaces on the inner surface side, and the bush 8 has a partial cylindrical surface having substantially the same curvature as the partial cylindrical surface of the bush holding portion 8A on the outer surface. It has a cylindrical member as a whole. The bush 8 is specifically composed of a pair of semi-cylindrical members. Two bushes 8 are provided, one of which is rotatably fitted in the bush holding portion 8A and the other is rotatably fitted in the bush holding portion 8B. The bush 8 sandwiches the plate-

like vane portions

4c and 5a between the pair of semi-columnar members, and the pair of semi-columnar members and the plate-like vane portion 4c slide to form a plate-like vane portion. 4c and 5a are held so as to be rotatable with respect to the first rotor 6A and the second rotor 7A and movable in a substantially normal direction.

Next, the compression operation of the vane type compressor 200 of the first embodiment will be described below. In FIG. 4, the rotor 6 and the cylinder inner peripheral surface 1a are closest to each other at one place (the closest point 32).

Here, the radius of the cylinder inner peripheral surface 1a is rc (see FIG. 4), the distance between the rotation center 4i of the vane shaft 4 and the vane tip 4d is rv (see FIG. 3 (a)), and the rotation center of the independent vane 5 Assuming that the distance between 5c and the vane tip 5b is rv (see FIG. 3A), rv is set to satisfy the following expression (1).

Rv = rc-δ ... (1)

δ is a gap between the

vane tip portions

4d and 5b and the cylinder inner peripheral surface 1a, and the

vane tip portions

4d and 5b come into contact with the cylinder inner peripheral surface 1a by setting rv as shown in Expression (1). Without rotating. Here, rv is set so that δ is as small as possible, and gas leakage from the

vane tip portions

4d and 5b is minimized.

As described above, the vane portion 4c and the cylinder inner peripheral surface 1a and the vane portion 5a and the cylinder inner peripheral surface 1a maintain a narrow gap, respectively, and the vane portion 4c and the vane portion 5a partition the inside of the cylinder 1. As a result, three spaces (suction chamber 9, intermediate chamber 10, and compression chamber 11) are formed in cylinder 1 (shown in FIG. 4). A suction port 1c is opened in the suction chamber 9 through a notch 1h. The notch 1h is provided from the vicinity of the closest point 32 in FIG. 4 (rotation angle 90 °) to the range of point B where the vane tip 4d and the cylinder inner peripheral surface 1a face each other.

Next, the rotation operation of the vane type compressor 200 according to the first embodiment will be described. Here, the vane shaft 4 is demonstrated as what rotates clockwise. The upper shaft portion 4 a of the vane shaft 4 receives rotational power from the drive portion of the electric element 102, and the vane portion 4 c rotates in the cylinder 1. Along with the rotation of the vane portion 4c, the rotational power is transmitted to the second rotor 7A via the bush 8 fitted to the bush holding portion 8A. Then, the rotational power transmitted to the second rotor 7A is transmitted to the first rotor 6A via the bush 8 and the independent vane 5 fitted to the bush holding portion 8B.

The rotor 6 receives a centrifugal force due to rotation, and the

rotor aligner portions

6c, 6d, 7c, 7d are pressed against the rotor

aligner bearing portions

2b, 3b and slide around the center of the rotor

aligner bearing portions

2b, 3b (see FIG. 4 around the rotation center 6 i of the rotor 6. The

vanes

4c and 5a rotate around the center of the shaft 4ab (upper shaft 4a and lower shaft 4b) (around the rotation center 4i in FIG. 4). Here, since the shaft portion 4ab and the cylinder inner peripheral surface 1a are concentric, the

vane portions

4c and 5a rotate around the center of the cylinder inner peripheral surface 1a (around the center 1f in FIG. 4). Then, the two bushes are arranged so that the extension lines in the radial direction (the left-right direction in FIG. 4) of the

vanes

4c and 5a are always directed to the cylinder center (center 1f of the cylinder inner peripheral surface 1a, center 1g of the cylinder outer peripheral surface). 8 rotates around the respective bush centers 8a in the

bush holding portions

8A and 8B.

In the above operation, the bush 8 fitted in the bush holding portion 8A and the side surface of the vane portion 4c slide with each other. Further, the bush 8 fitted in the bush holding portion 8B and the side surface of the vane portion 5a slide on each other. Then, the outer peripheral surface of the bush 8 fitted into the bush holding portion 8A, the end surface 6e of the first rotor 6A and the end surface 7e of the second rotor 7A constituting the bush holding portion 8A slide with each other. Further, the outer peripheral surface of the bush 8 fitted into the bush holding portion 8B, the end surface 6f of the first rotor 6A and the end surface 7f of the second rotor 7A constituting the bush holding portion 8B slide with each other.

FIG. 5 is a diagram showing the first embodiment of the present invention, showing a compression operation of the vane type compressor 200, and a cross-sectional view taken along the line II of FIG. The manner in which the volumes of the suction chamber 9, the intermediate chamber 10, and the compression chamber 11 change will be described with reference to FIG. In FIG. 5, directions and positions where suction, discharge, and inflow are performed are indicated by white arrows.

First, as the vane shaft 4 rotates, low-pressure gas flows from the suction pipe 26 into the suction port 1c. Here, the rotation angle in FIG. 5 is the closest point 32 where the rotor 6 and the cylinder inner peripheral surface 1a are closest to each other, and one portion where the vane portion 4c of the vane shaft 4 and the cylinder inner peripheral surface 1a face each other. When they coincide, it is defined as “angle 0 °”. In FIG. 5, the positions of the

vanes

4c and 5a at “angle 0 °”, “angle 90 °”, “angle 180 °”, and “angle 270 °”, and the suction chamber 9, the intermediate chamber 10, and The state of the compression chamber 11 is shown. Further, in the “angle 0 °” diagram of FIG. 5, the rotation direction of the vane shaft 4 (clockwise in FIG. 5) is indicated by an arrow, but the arrow is omitted in other drawings.

In “angle 0 °” in FIG. 5, the right space partitioned by the closest contact 32 and the vane portion 4c is the suction chamber 9, and the suction chamber 9 communicates with the suction port 1c via the notch 1h. Inhale gas. The left space partitioned by the closest contact 32 and the vane portion 4c is a compression chamber 11 communicating with the discharge port 2d (shown in FIG. 1).

At “angle 90 °” in FIG. 5, the vane tip portion 4d of the vane portion 4c overlaps the point B on the cylinder inner peripheral surface 1a, so that the suction chamber 9 does not communicate with the suction port 1c. Thereby, the suction of the gas is finished, and the suction chamber 9 becomes the intermediate chamber 10. In this state, the volume of the intermediate chamber 10 is substantially maximum. In this state, a suction chamber 9 is newly generated on the side opposite to the intermediate chamber 10 with the vane portion 4c as a boundary. As the vane shaft 4 rotates, the volume of the suction chamber 9 increases and suction continues. Further, since the volume of the compression chamber 11 becomes smaller than that at the “angle 0 °”, the gas in the compression chamber 11 is compressed.

Thus, since the volume of the compression chamber 11 continues to decrease as the vane shaft 4 rotates, the gas is compressed and its pressure gradually increases. When the pressure in the compression chamber 11 exceeds the high pressure of the refrigeration cycle, a discharge valve (not shown) is opened, and the gas in the compression chamber 11 is discharged into the sealed container 103 from the discharge port 2d. Here, the gas discharged into the sealed container 103 passes through the electric element 102 and is discharged to the outside (high pressure side of the refrigeration cycle) from the discharge pipe 24 fixed (welded) to the upper part of the sealed container 103 ( (Indicated by solid lines in FIG. 1). Therefore, the pressure in the sealed container 103 is a high discharge pressure. FIG. 5 shows a case where the pressure in the compression chamber 11 exceeds the high pressure at an “angle of 0 °”.

At “angle 180 °” in FIG. 5, the suction chamber 9 shifts to the intermediate chamber 10, the intermediate chamber 10 shifts to the compression chamber 11, and thereafter, the vane portion 4 c, the vane portion 5 a, and the rotor at “angle 0 °”. The compression operation is repeated with the rotor 6 and the rotor 7 switched.

In the above operation, the oil pump 31 is driven by the rotation of the vane shaft 4, and the refrigerating machine oil 25 is sucked up from the oil reservoir 104 by the oil pump 31 and sent out to the oil supply passage 4e as shown by the broken line in FIG. The refrigerating machine oil 25 sent out to the oil supply passage 4e passes through the oil supply passage 4f and is sent out to the recess 2a of the frame 2 through the recess 3a of the cylinder head 3 and the oil supply passage 4g.

The refrigerating machine oil 25 fed to the

recesses

2a and 3a lubricates the rotor

aligner bearing portions

2b and 3b. Further, the refrigerating machine oil 25 is supplied to a rotor inner space which is a space communicating with the

recesses

2a and 3a and surrounded by the rotor inner peripheral surface 6b and the rotor inner peripheral surface 7b. Here, since the pressure in the hermetic container 103 is a high discharge pressure, the pressure in the

recesses

2a and 3a and the pressure in the rotor inner space are also discharge pressures. A part of the refrigerating machine oil 25 fed to the

recesses

2 a and 3 a is supplied to the main bearing portion 2 c of the frame 2 and the main bearing portion 3 c of the cylinder head 3.

FIG. 6 is a diagram showing the first embodiment of the present invention, and is a cross-sectional view of the main part around the vane portion 4c in FIG. In the figure, arrows indicated by solid lines indicate the flow of the refrigerating machine oil 25.
The pressure in the rotor inner space is the discharge pressure as described above, and is higher than the pressure in the suction chamber 9 and the intermediate chamber 10. For this reason, the refrigerating machine oil 25 is sent out to the suction chamber 9 and the intermediate chamber 10 by the pressure difference and the centrifugal force while lubricating the sliding portion between the side surface of the vane portion 4 c and the bush 8. Further, the refrigerating machine oil 25 lubricates the sliding portion between the bushing 8 and the end surface 6e of the first rotor 6A and the end surface 7e of the second rotor 7A that form the bush holding portion 8A, while the pressure difference and centrifugal force are reduced. It is sent out to the suction chamber 9 and the intermediate chamber 10 by force. A part of the refrigerating machine oil 25 fed to the intermediate chamber 10 flows into the suction chamber 9 while sealing the gap between the vane tip 4d and the cylinder inner peripheral surface 1a.

Further, in the above, the case where the space partitioned by the vane portion 4 c is the suction chamber 9 and the intermediate chamber 10 has been described. However, the rotation proceeds and the space partitioned by the vane portion 4 c becomes the intermediate chamber 10 and the compression chamber 11. The same applies to cases. Even when the pressure in the compression chamber 11 reaches the same discharge pressure as the pressure in the rotor inner space, the refrigerating machine oil 25 is sent out toward the compression chamber 11 by centrifugal force. Although the above operation is shown for the vane unit 4c, the same operation is performed in the vane unit 5a.

In the above, as shown in FIG. 1, the refrigerating machine oil 25 supplied to the main bearing portion 2 c is discharged to the space above the frame 2 through the gap of the main bearing portion 2 c and then provided on the outer peripheral portion of the cylinder 1. Returned to the oil sump 104 through the oil return hole 1e. Further, the refrigerating machine oil 25 supplied to the main bearing portion 3c is returned to the oil sump 104 through the gap of the main bearing portion 3c. The refrigerating machine oil 25 sent to the suction chamber 9, the intermediate chamber 10 and the compression chamber 11 via the rotor inner space is finally discharged together with the gas from the discharge port 2d to the space above the frame 2. The refrigerating machine oil 25 discharged into the space above the frame 2 is returned to the oil sump 104 through the oil return hole 1e provided in the outer peripheral portion of the cylinder 1. Of the refrigerating machine oil 25 sent to the oil supply passage 4 e by the oil pump 31, the surplus refrigerating machine oil 25 is discharged from the oil drain hole 4 h above the vane shaft 4 to the space above the frame 2, and then cylinder 1 is returned to the oil sump 104 through an oil return hole 1e provided in the outer periphery of the oil reservoir 1.

The first embodiment is configured as described above. For example, as described in Patent Document 1, the rotation center of the shaft and the center of the cylinder inner peripheral surface are eccentric to each other. The difference from the machine will be described below.

In the case of the configuration described in Patent Document 1, as described above, the reason why the cylinder wall thickness is not uniform in the circumferential direction is that the center of the cylinder inner peripheral surface is the center of rotation of the shaft (of the sealed container). This is because it is eccentric with respect to the center. That is, since the outer peripheral surface of the cylinder is fixed to the sealed container, the center of the cylinder coincides with the center of the sealed container, and the shaft center is positioned at the center of the sealed container from the viewpoint of structural balance. Is placed. And in patent document 1, the shaft and the rotor are united, and both are comprised coaxially.

In a vane type compressor in which the tip of the vane and the inner peripheral surface of the cylinder can operate without contact, the center of the inner peripheral surface of the cylinder is eccentric from the rotation center of the rotor in order to realize the operation of reducing the compression chamber. There is a premise to do. Since the rotor is integrally formed coaxially with the shaft as described above, the center of the inner peripheral surface of the cylinder must be decentered from the rotation center (shaft center) of the rotor. And, the cylinder thickness on the direction side where the cylinder inner peripheral surface is eccentric with respect to the rotation center of the shaft (that is, the side where the thickness is reduced) may be set to a thickness at which at least the necessary strength can be obtained. The cylinder thickness on the side opposite to the direction of eccentricity (that is, the side where the thickness is increased) needs to be thicker than the thickness capable of obtaining the required strength. Therefore, the diameter of the cylinder outer periphery is increased, and the diameter of the sealed container is increased correspondingly to increase the diameter of the cylinder outer periphery.

On the other hand, in the first embodiment, the rotation center 6i of the rotor 6 and the rotation center 4i of the vane shaft 4 are eccentric, and the rotation center 4i of the vane shaft 4 and the center 1f of the cylinder inner peripheral surface 1a are formed. Matched structure. For this reason, cylinder thickness can be uniformly set to the thickness which can obtain required intensity over the whole circumferential direction. Therefore, when the cylinder internal volume is the same in the conventional structure in which the rotation center 4i of the vane shaft 4 and the center 1f of the cylinder inner peripheral surface 1a are eccentric and in the structure of the first embodiment in which the eccentricity is not eccentric, The structure of form 1 can reduce the diameter of the cylinder outer periphery. As a result, the sealed container 103 can be reduced in size.

Here, the

vane portions

4c and 5a provided in the cylinder 1 always realize the structure in which the

vane portions

4c and 5a are directed to the center 1f of the cylinder inner peripheral surface 1a from the viewpoint of reducing sliding, and the rotation center 4i of the vane shaft 4 and the cylinder inner peripheral surface. The structure adopted in the first embodiment is arranged in order to make the structure coincident with the center 1f of 1a.

In the first embodiment, first, the shaft portion 4ab and the rotor 6 are separated. And it was set as the structure which the shaft part 4ab and the vane part 4c rotate integrally. Further, the vane portion 4c is supported by the rotor 6 so as to be rotatable around the center 1f of the inner peripheral surface 1a of the cylinder 1 and movable in the radial direction of the cylinder 1, and the rotation of the shaft portion 4ab is first transmitted to the vane portion 4c. And it was set as the structure which rotates the

rotor parts

6j and 7j and the vane part 5a via the vane part 4c. For this reason, the rotation center 6 i of the rotor 6 can be structured to be eccentric from the rotation center 4 i of the vane shaft 4.

As described above, in the first embodiment, the rotation center 6i of the rotor 6 and the rotation center 4i of the vane shaft 4 are eccentric, and the rotation center 4i of the vane shaft 4 and the center 1f of the cylinder inner peripheral surface 1a. And the structure matched. As a result, the cylinder wall thickness can be made uniform, the cylinder outer periphery can be made smaller than the conventional structure for the same cylinder volume, and the sealed container 103 can be made smaller accordingly. is there.

Furthermore, in the first embodiment, the

vane portions

4c and 5a are rotatable around the center 1f of the inner peripheral surface 1a of the cylinder 1, and the

vane portions

4c and 5a are rotatable with respect to the rotor 6. Moreover, since the bush 8 is supported so as to be movable in the radial direction of the cylinder 1 relative to the rotor 6, the

vane tip portions

4d and 5b operate without contact with the cylinder inner peripheral surface 1a. Therefore, a highly efficient vane type compressor with very little sliding loss can be obtained in the same manner as in Patent Document 1.

Embodiment 2. FIG.
FIG. 7 is a diagram showing the second embodiment of the present invention, and is an exploded perspective view of the compression element 101 of the vane type compressor 200. In the second embodiment, only the configuration different from the first embodiment will be described.

In the second embodiment, the

rotor aligner portions

6c and 6d are formed by arc-shaped convex portions that are thinner than the thickness of the rotor portion 6j of the first rotor 6A, and the rotor portion 6j is positioned on the rotation center side on each of the upper and lower end surfaces. They are arranged. The outer peripheral surfaces of the

rotor aligner portions

6c and 6d are discontinuous with the outer peripheral surface 6a of the rotor portion 6j. The rotor aligners 7c and 7d are arc-shaped convex portions that are thinner than the thickness of the rotor portion 7j of the second rotor 7A, and are arranged close to the rotation center side on the upper and lower end surfaces of the rotor portion 7j. Yes. The outer peripheral surfaces of the

rotor aligner portions

7c and 7d are discontinuous with the outer peripheral surface 7a of the rotor portion 7j.

The second embodiment configured as described above can obtain the same effects as those of the first embodiment and the following effects. That is, since the diameter of the

rotor aligners

6c, 6d, 7c, and 7d can be reduced as compared with the first embodiment, the bearing loss can be reduced by reducing the peripheral speed at the

rotor aligner bearings

2b and 3b.

Embodiment 3 FIG.
FIG. 8 is a diagram showing the third embodiment of the present invention, and is a cross-sectional view at a rotation angle of 90 °. 9A and 9B are diagrams showing Embodiment 3 of the present invention, in which FIG. 9A is a plan view of the independent vane 5 and FIG. 9B is a front view of the independent vane 5. In the third embodiment, only the configuration different from the first embodiment will be described.

In the third embodiment, the independent vane 5 has the same configuration as the vane described in Patent Document 1. That is, the independent vane 5 includes a substantially square plate-like vane portion 5a and a pair of arc-shaped

rotation support portions

5e and 5f. The

rotation support portions

5e and 5f are respectively fixed to the upper and lower end surfaces of the vane portion 5a. The vane length direction of the vane portion 5a (the left-right direction in FIG. 8) and the normal direction of the arc of the vane tip 5b are formed so as to pass through the centers of the arcs forming the

rotation support portions

5e and 5f. The center of the arc forming the

rotation support portions

5e and 5f is formed so as to pass through the central axis of the shaft portion 4ab.

Further, the end surface of the frame 2 on the cylinder 1 side has a recess into which the rotation support portion 5e is slidably fitted in the circumferential direction, and the end surface of the cylinder head 3 on the cylinder 1 side is provided with a rotation support portion 5f. It has a recess that is held so as to be movable in the circumferential direction.

When the shaft portion 4ab of the vane shaft 4 rotates, the vane portion 4c rotates in the cylinder 1, and the independent vane 5 rotates along with the rotation. The independent vane 5 rotates in a state in which the direction of the vane portion 5a is regulated so that the normal line of the arc at the tip of the vane portion 5a always coincides with the normal line of the cylinder inner peripheral surface 1a.

The third embodiment configured as described above can obtain the same effects as those of the first embodiment and the following effects. That is, the shaft diameters of the

rotation support portions

5e and 5f can be increased compared with the rotation support portion 5d of the first embodiment. For this reason, the peripheral speed of the rotation support portion 5d can be increased, and therefore, an oil film can be easily formed at the bearing portions of the

rotation support portions

5e and 5f, and fluid lubrication can be promoted. For this reason, in the configuration of the first embodiment, when fluid lubrication in the rotation support portion 5d is not established, the configuration of the third embodiment can reduce the bearing loss and improve the reliability of the bearing.

The vane type compressor of the present invention is not limited to the structure shown in each of the above drawings, and can be variously modified as follows without departing from the gist of the present invention.

(Modification 1)
FIG. 10 is a view showing a modified example of the vane type compressor 200 according to Embodiments 1 to 3 of the present invention, and is a view showing the arrangement of the vane shaft 4 and the independent vanes 5. 10A is a front view of the vane shaft 4 and the independent vane 5, FIG. 10B is a cross-sectional view taken along the line II in FIG. 10A, and FIG. 10C is a cross-sectional view taken along the line II- in FIG. It is II sectional drawing.
In the first to third embodiments, the joint portion between the shaft portion 4ab and the vane portion 4c is configured in a columnar shape, but is not limited to this shape, and any shape can be adopted. For example, as shown in FIG. 10, the joint portion between the shaft portion 4ab and the vane portion 4c may be, for example, a substantially rectangular shape. And the rigidity of a junction part is securable by making the junction part comprised in the substantially rectangular shape large compared with the case where it makes the column shape of FIG.

(Modification 2)
In the first to third embodiments, the case where the vane portion 4c and the shaft portion 4ab are integrally formed has been described. However, the vane portion 4c and the shaft portion 4ab are separately formed, and the two portions are integrally formed with each other. It is good also as the assembled structure. In short, the vane portion 4c and the shaft portion 4ab may be configured to rotate integrally. With this configuration, the same effect can be obtained.

(Modification 3)
FIG. 11 is a diagram showing a modification of the vane type compressor 200 according to Embodiments 1 to 3 of the present invention. The vane type compressor of the modification is taken along the line II of FIG. 1 at a rotation angle of 90 °. It is sectional drawing cut | disconnected by the line | wire of the same position as a line. In the first to third embodiments, the case where the number of vanes is two has been described. However, when the number of vanes is one as shown in FIG. 11, the number of parts can be further reduced. Alternatively, in the configuration in which the number of vanes is three or more, leakage loss due to a pressure difference across the vanes can be reduced by increasing the number of compression chambers, and further efficiency can be improved.

(Modification 4)
In the first to third embodiments, the oil pump 31 using the centrifugal force of the vane shaft 4 has been described. However, the oil pump 31 may have any form, for example, a volume described in Japanese Patent Application Laid-Open No. 2009-6282. A shape pump may be used as the oil pump 31.

(Modification 5)
In the first to third embodiments, the bush 8 is composed of a pair of semi-cylindrical members separated from each other. However, the ends of the pair of semi-cylindrical members are connected to each other. You may comprise. With such a configuration, the number of parts can be reduced.

(Modification 6)
In the first to third embodiments, the

rotors

6 and 7 are divided in the circumferential direction. However, the end portions of the first rotor 6A and the second rotor 7A are connected to each other so as to be integrated. May be. With such a configuration, the number of parts can be reduced.

1 cylinder, 1a cylinder inner surface, 1c suction port, 1d discharge communication flow path, 1e oil return hole, 1f cylinder inner surface center, 1g cylinder outer surface center, 1h notch, 2 frame, 2a recess, 2b Rotor aligner bearing part, 2c main bearing part, 2d discharge port, 2e discharge valve, 3 cylinder head, 3a recess, 3b inner peripheral surface (rotor aligner bearing part), 3c main bearing part, 4 vane shaft, 4a upper shaft part 4ab shaft section, 4b lower shaft section, 4c vane section, 4d vane tip section, 4e oil supply path, 4f oil supply path, 4g oil supply path, 4h oil discharge hole, 4i vane shaft rotation center, 5 independent vane, 5a vane Part (independent vane part), 5b vane tip, 5c independent vane rotation center, 5d rotation Holding section, 5e rotation support section, 5f rotation support section, 6 rotor, 6A first rotor, 6a outer peripheral surface, 6b rotor inner peripheral surface, 6c rotor aligner section, 6d rotor aligner section, 6e circumferential direction of first rotor End face, 6f end face in the circumferential direction of the first rotor, 6g vane relief face, 6h vane relief face, 6i rotor center of rotation, 6j rotor section, 7 rotor, 7A second rotor, 7a outer circumference face, 7b in the rotor Peripheral surface, 7c Rotor aligner, 7d Rotor aligner, 7e End surface of second rotor in circumferential direction, 7f End surface of second rotor, 7g vane relief surface, 7h vane relief surface, 7j rotor portion, 8 bush, 8A Bush holder, 8B Bush holder, 9 Suction chamber, 10 Intermediate chamber, 11 Compression chamber, 21 Stator, 22 Rotor, 23 Glass terminals, 24 discharge pipe, 25 refrigerating machine oil, 26 intake pipe, 31 an oil pump, 32 nearest point, 101 compression element 102 electric element 103 closed vessel, sump 104 oil, 200 vane compressor.

Claims

A cylindrical cylinder with both axial ends open;
A cylinder head and a frame for closing both axial ends of the cylinder;
A shaft portion whose rotational center coincides with the center of the inner peripheral surface of the cylinder and rotates in the cylinder;
A vane portion that rotates integrally with the shaft portion;
A rotor whose center of rotation is eccentric from the center of the inner peripheral surface of the cylinder, is inserted through the space around the shaft portion, and rotates in the cylinder;
A bush that is installed on the rotor and supports the vane portion so as to be rotatable with respect to the rotor and movable in the radial direction of the cylinder;
The vane portion extends from the shaft portion through the bush toward the inner peripheral surface of the cylinder,
The rotor is a vane type compressor that rotates when the rotational force of the shaft portion is transmitted through the vane portion and the bush.
The frame and the cylinder head have a concave portion eccentric to the inner peripheral surface of the cylinder on an end surface on the cylinder side,
2. The vane compressor according to claim 1, wherein the rotor includes a rotor aligner portion inserted into the concave portion at an end portion on the frame side and an end portion on the cylinder head side of the rotor.
The rotor is configured in an annular shape,
The rotor aligner portion has an arc shape whose thickness in the radial direction is thinner than the thickness in the radial direction of the rotor;
The vane compressor according to claim 2, wherein the recess is a ring-shaped groove.
The vane type compressor according to any one of claims 1 to 3, further comprising a vane shaft having the vane portion and the shaft portion.
The rotor has a cylindrical bush holding portion penetrating in the axial direction, and the bush formed of a pair of semi-columnar members is rotatably fitted in the bush holding portion, The vane portion is sandwiched between cylindrical members, and the vane portion is slidably supported, so that the vane portion can rotate around the center of the inner peripheral surface of the cylinder and the radial direction of the cylinder The vane type compressor according to any one of claims 1 to 4, wherein the rotor is supported by the rotor so as to be movable.
6. The vane compressor according to claim 5, wherein the bush is integrally formed by connecting ends of the pair of semi-cylindrical members.
The rotor includes a first rotor and a second rotor obtained by dividing a ring-shaped member in the circumferential direction, and ends of the first rotor and the second rotor are connected to each other to be integrated. The vane type compressor according to any one of claims 1 to 6, wherein:
The vane type compressor according to any one of claims 1 to 7, wherein an independent vane that rotates concentrically with the vane portion is provided in the cylinder.
The said independent vane is provided with the independent vane part and the hollow cylindrical rotation support part provided in the rotation center side of the said independent vane part, The said shaft part is rotatably inserted in the said rotation support part. Item 9. A vane compressor according to Item 8.
The independent vane includes an independent vane portion and a pair of arc-shaped rotation support portions that support the independent vane portion,
The frame and the cylinder head each have a concave portion in which the rotation support portion is slidably fitted in an end surface on the cylinder side and the inner peripheral surface is eccentric with respect to the inner peripheral surface of the cylinder. The vane type compressor according to claim 8, comprising: