WO2019187686A1

WO2019187686A1 - Compressor

Info

Publication number: WO2019187686A1
Application number: PCT/JP2019/004399
Authority: WO
Inventors: 山本　真也; 和也本田; 健吾榊原; 小林　裕之; 謙並木
Original assignee: 株式会社豊田自動織機
Priority date: 2018-03-30
Filing date: 2019-02-07
Publication date: 2019-10-03
Also published as: DE112019001729T5; JPWO2019187686A1; US20210164471A1

Abstract

This compressor is provided with: a rotating shaft; a front rotor which has a front rotor surface; an intermediate wall section which has a first wall surface facing the front rotor surface in an axial direction; and a vane which is inserted in a vane groove formed in the intermediate wall section and which moves in the axial direction as the front rotor rotates. The vane has a first vane end section, the first vane end section being the end section thereof in the axial direction, which is in contact with the front rotor surface. The first vane end section is curved to protrude toward the front rotor surface and extends in a direction perpendicular to the axial direction. The front rotor surface includes a front curved surface which is curved in the axial direction Z so as to be displaced in the axial direction in accordance with the angular position of the front rotor surface.

Description

Compressor

The present invention relates to a compressor.

Patent Document 1 includes a rotating shaft, a rotor that has a rotor surface and rotates as the rotating shaft rotates, a vane that moves in the axial direction of the rotating shaft as the rotor rotates, and a compression chamber. The compressor is described. In this compressor, the fluid is compressed in the compression chamber by rotating the rotor.

In this document, as a third embodiment, the position of the straight line extending in the radial direction continuously decreases from the first angle position to the first angle position of the rotor, and from the first angle position to the first angle position. Until now, a rotor surface composed of a curved surface that continuously increases and a vane having an end abutting against the rotor surface are described.

In the above configuration, the vane easily swings in the circumferential direction of the rotor around the radially extending portion where the rotor surface and the end of the vane abut.

JP 51-97006 A

An object of the present invention is to provide a compressor capable of suppressing the vane from swinging in the circumferential direction of the rotor.

In order to solve the above-described problems, according to a first aspect of the present invention, a rotating shaft, a rotor surface formed in a ring shape, and a rotor that rotates as the rotating shaft rotates, An outer peripheral surface and an inner peripheral surface facing the radial direction of the rotating shaft; a cylindrical portion that houses the rotor; a wall portion having a wall surface facing the rotor surface and the axial direction of the rotating shaft; and the wall The vane is inserted into a vane groove formed in the portion and moved in the axial direction along with the rotation of the rotor, and is partitioned by the rotor surface, the wall surface, and the inner peripheral surface of the cylindrical portion, And a compression chamber in which a change in volume is caused by the vane to suck and compress a fluid, and the vane has an end portion in the axial direction and a vane end portion that comes into contact with the rotor surface, The vane end faces the rotor surface And the rotor surface includes a curved surface curved in the axial direction, and the curved surface is displaced in the axial direction according to the angular position. The curved surface includes a concave surface curved in the axial direction so as to be concave toward the wall surface, and a convex surface curved in the axial direction so as to be convex toward the wall surface. The concave surface has a concave inner peripheral edge and a concave outer peripheral edge as both ends in the radial direction, and the curvature radius of the concave inner peripheral edge in the axial direction is larger than the curvature radius of the concave outer peripheral edge in the axial direction. The convex surface has a convex inner peripheral edge and a convex outer peripheral edge as both ends in the radial direction, and the convex surface has a radius of curvature of the convex inner peripheral edge in the axial direction from a curvature radius of the convex outer peripheral edge. A small compressor is provided.

In order to solve the above-described problem, according to a second aspect of the present invention, a rotating shaft, a rotor surface formed in a ring shape, which rotates as the rotating shaft rotates, and the rotor An outer peripheral surface and an inner peripheral surface facing the radial direction of the rotating shaft; a cylindrical portion that houses the rotor; a wall portion having a wall surface facing the rotor surface and the axial direction of the rotating shaft; and the wall The vane is inserted into a vane groove formed in the portion and moved in the axial direction along with the rotation of the rotor, and is partitioned by the rotor surface, the wall surface, and the inner peripheral surface of the cylindrical portion, And a compression chamber in which a change in volume is caused by the vane to suck and compress a fluid, and the vane has an end portion in the axial direction and a vane end portion that comes into contact with the rotor surface, The vane end faces the rotor surface And the rotor surface includes a curved surface curved in the axial direction, and the curved surface is displaced in the axial direction according to the angular position. The curved surface with respect to the axial direction according to the radial position so that at least a part of the contact line between the curved surface and the vane end portion bends in the circumferential direction of the rotor. A compressor is provided that includes portions with different radii of curvature.

Sectional drawing which shows the outline | summary of a compressor. The exploded perspective view of main composition. The disassembled perspective view of the main structures seen from the opposite side to FIG. The elements on larger scale of FIG. FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 4 in a non-communication state. FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 4 in a communication state. Sectional drawing which shows typically the contact aspect of a vane and both curved surfaces. The graph which shows the displacement of the axial direction according to the angular position in a rotor surface. The front view of a front rotor. The front view of a rear rotor. Sectional drawing which shows the periphery structure of both rotors at the time of cut | disconnecting in the vicinity of an inflection point. The schematic diagram which shows the front contact line seen from the axial direction. The schematic diagram which shows the rear contact line seen from the axial direction. (A) is sectional drawing which shows both rotors and its periphery, (b) is a development view which shows the state of both rotors and vanes in the state of (a). (A) is sectional drawing which shows both rotors and its periphery, (b) is a development view which shows the state of both rotors and vanes in the state of (a). The graph which shows volume change. The schematic diagram which shows another example of a communication mechanism. The schematic diagram which shows another example of a communication mechanism. Sectional drawing which shows the compressor of another example typically. Sectional drawing which shows the vane of another example typically. The elements on larger scale of FIG. Sectional drawing which shows the vane of another example typically.

Hereinafter, an embodiment of a compressor will be described with reference to the drawings. The compressor of this embodiment is mounted and used in a vehicle. The compressor is used in a vehicle air conditioner. The fluid to be compressed by the compressor is a refrigerant containing oil. 1 and 4 show side views of the rotating shaft 12 and the

rotors

60 and 80. FIG.

As shown in FIG. 1, the compressor 10 includes a housing 11, a rotating shaft 12, an electric motor 13, an inverter 14, a front cylinder 40, a rear cylinder 50, a front rotor 60 as a first rotor, And a rear rotor 80 as a second rotor. The housing 11 has a cylindrical shape as a whole, and has a suction port 11a through which suction fluid from the outside is sucked and a discharge port 11b through which fluid is discharged. The rotating shaft 12, the electric motor 13, the inverter 14, both

cylinders

40 and 50, and both

rotors

60 and 80 are accommodated in the housing 11.

The housing 11 includes a front housing 21, a rear housing 22, and an inverter cover 23. The front housing 21 has a bottomed cylindrical shape and opens toward the rear housing 22. The suction port 11a is provided at a position between the opening end and the bottom of the side wall of the front housing 21. The position of the suction port 11a is arbitrary. The rear housing 22 has a bottomed cylindrical shape and opens toward the front housing 21. The discharge port 11 b is provided on the side surface of the bottom portion of the rear housing 22. The position of the discharge port 11b is arbitrary.

The front housing 21 and the rear housing 22 are unitized with their openings facing each other. The inverter cover 23 is disposed at the bottom of the front housing 21 that is opposite to the rear housing 22. The inverter cover 23 is fixed to the front housing 21 in a state of being abutted against the bottom of the front housing 21.

The inverter 14 is accommodated in the inverter cover 23. The inverter 14 drives the electric motor 13. The rotating shaft 12 is supported by the housing 11 in a rotatable state. A ring-shaped first bearing holding portion 31 protruding from the bottom portion is provided at the bottom portion of the front housing 21. A first radial bearing 32 that rotatably supports the first end of the rotating shaft 12 is provided on the radially inner side of the first bearing holding portion 31. A ring-shaped second bearing holding portion 33 protruding from the bottom portion is provided at the bottom portion of the rear housing 22. A second radial bearing 34 is also provided on the radially inner side of the second bearing holding portion 33. The second radial bearing 34 rotatably supports the second end portion on the side opposite to the first end portion of the rotating shaft 12. The axial direction Z of the rotating shaft 12 coincides with the axial direction of the housing 11.

As shown in FIGS. 1 to 4, the front cylinder 40 houses a front rotor 60. The front cylinder 40 has a bottomed cylindrical shape that is slightly smaller than the rear housing 22. The front cylinder 40 opens toward the bottom of the rear housing 22. The front cylinder 40 has a front cylinder bottom 41 and a front cylinder side wall 42 extending from the front cylinder bottom 41 toward the rear housing 22. The front cylinder side wall portion 42 is a first cylinder portion and enters the inside of the rear housing 22.

3 and 4, the front cylinder 40 has a front cylinder inner peripheral surface 43 as a first inner peripheral surface. The front cylinder inner peripheral surface 43 is a cylindrical surface extending in the axial direction Z. The front cylinder 40 further has a front diameter-enlarged surface 44 that is larger in diameter than the front cylinder inner circumferential surface 43. The front diameter-enlarging surface 44 is provided at the front end (opening end) of the front cylinder side wall 42. A front step surface 45 is formed between the front cylinder inner peripheral surface 43 and the front enlarged diameter surface 44.

The front cylinder side wall portion 42 is provided with a bulging portion 46 protruding outward in the radial direction of the rotary shaft 12. The bulging portion 46 is provided at the base end of the front cylinder side wall portion 42, that is, near the front cylinder bottom portion 41. The front housing 21 and the rear housing 22 are unitized with the bulging portion 46 interposed therebetween. Both the

housings

21 and 22 restrict the positional deviation of the front cylinder 40 in the axial direction Z.

As shown in FIG. 4, the front cylinder bottom 41 is stepped in the axial direction Z. The front cylinder bottom 41 includes a first bottom 41a disposed on the center side, a second bottom 41b disposed radially outside the first bottom 41a and closer to the rear housing 22 than the first bottom 41a. have. The first bottom portion 41a is formed with a front insertion hole 41c through which the rotary shaft 12 can be inserted. The rotating shaft 12 is inserted through the front insertion hole 41c.

As shown in FIG. 1, the front housing 21 and the front cylinder bottom 41 form a motor chamber A1, and the electric motor 13 is accommodated in the motor chamber A1. The electric motor 13 rotates the rotating shaft 12 in the direction indicated by the arrow M when the driving power is supplied from the inverter 14. The suction port 11a is provided in the front housing 21 that forms the motor chamber A1. For this reason, the suction fluid sucked from the suction port 11a is introduced into the motor chamber A1. That is, the suction fluid exists in the motor chamber A1.

In the compressor 10, the inverter 14, the electric motor 13, and both the

rotors

60 and 80 are arranged in order in the axial direction Z. The position of each of these components is arbitrary, and the inverter 14 may be disposed outside the electric motor 13 in the radial direction.

As shown in FIGS. 2 to 4, the rear cylinder 50 has a bottomed cylindrical shape opened toward the bottom of the rear housing 22. The rear cylinder 50 is formed slightly smaller than the front cylinder 40 and is accommodated in the rear housing 22. The rear cylinder 50 is fitted to the front cylinder 40 with the opening end of the rear cylinder 50 butted against the bottom of the rear housing 22.

The rear cylinder 50 has an intermediate wall 51 that forms the bottom of the rear cylinder 50, and a rear cylinder side wall 55 that extends from the intermediate wall 51 toward the rear housing 22 in the axial direction Z. The rear cylinder side wall portion 55 corresponds to the second tube portion, and the intermediate wall portion 51 corresponds to the wall portion.

As shown in FIG. 4, the intermediate wall 51 is arranged with the wall thickness direction aligned with the axial direction Z. For this reason, the intermediate wall portion 51 has a first wall surface 52 and a second wall surface 53 that are orthogonal to the axial direction Z. The intermediate wall portion 51 has a ring shape and is fitted to the front cylinder 40. In the intermediate wall portion 51, a wall portion through hole 54 penetrating in the axial direction Z is formed. The wall portion through hole 54 is a through hole having a diameter larger than that of the rotating shaft 12. The rotating shaft 12 is inserted through the wall through hole 54.

The rear cylinder side wall 55 has a cylindrical shape extending in the axial direction Z, and has a rear cylinder inner peripheral surface 56 as a second inner peripheral surface and a rear cylinder outer peripheral surface 57. The rear cylinder inner peripheral surface 56 is a cylindrical surface having a smaller diameter than the front cylinder inner peripheral surface 43. For this reason, the rear cylinder inner peripheral surface 56 is disposed on the radially inner side of the front cylinder inner peripheral surface 43. The rear cylinder outer peripheral surface 57 has a step shape because it is a plurality of cylindrical surfaces having different diameters. The rear cylinder outer peripheral surface 57 includes a first part surface 57a, a second part surface 57b having a diameter larger than that of the first part surface 57a, and a third part surface 57c having a diameter larger than that of the second part surface 57b. Have.

The first part surface 57 a is in contact with the inner peripheral surface 43 of the front cylinder. The second part surface 57b is in contact with the front enlarged diameter surface 44. The third part surface 57c is flush with the outer peripheral surface of the front cylinder side wall 42. The first rear step surface 58 formed between the two

part surfaces

57a and 57b contacts the front step surface 45, and the second rear step surface 59 formed between the two part surfaces 57b and 57c serves as the front cylinder 40. It is in contact with the open end of.

As shown in FIG. 4, the front cylinder bottom 41, the front cylinder inner peripheral surface 43, and the first wall surface 52 form a front storage chamber A <b> 2 that stores the front rotor 60. The front storage chamber A2 has a cylindrical shape as a whole. The inner bottom surface of the rear housing 22, the rear cylinder inner peripheral surface 56, and the second wall surface 53 form a rear housing chamber A <b> 3 that houses the rear rotor 80. The rear housing chamber A3 has a cylindrical shape as a whole.

Since the diameter of the rear cylinder inner peripheral surface 56 is smaller than the diameter of the front cylinder inner peripheral surface 43, the rear storage chamber A3 is smaller than the front storage chamber A2, and the volume of the rear storage chamber A3 is larger than the volume of the front storage chamber A2. small. Both storage chambers A2 and A3 are partitioned by an intermediate wall 51. Both the

rotors

60 and 80 are disposed so as to face the axial direction Z with the intermediate wall 51 disposed therebetween.

Rotating shaft 12 and both

rotors

60 and 80 have the same axis. That is, the compressor 10 has a structure of an axial movement, not an eccentric movement. The circumferential direction of both

rotors

60 and 80 coincides with the circumferential direction of the rotary shaft 12, the radial direction of both

rotors

60 and 80 coincides with the radial direction R of the rotary shaft 12, and the axial direction of both

rotors

60 and 80 is the rotational axis. 12 coincides with the axial direction Z. For this reason, the circumferential direction, radial direction R, and axial direction Z of the rotating shaft 12 may be appropriately read as the circumferential direction, radial direction, and axial direction of the

rotors

60 and 80.

As shown in FIGS. 2 to 4, the front rotor 60 is ring-shaped and has a front through-hole 61 through which the rotary shaft 12 can be inserted. The front through hole 61 has the same diameter as the rotary shaft 12. The front rotor 60 is attached to the rotary shaft 12 with the rotary shaft 12 inserted through the front through hole 61.

The front rotor 60 rotates as the rotating shaft 12 rotates. That is, the front rotor 60 rotates integrally with the rotating shaft 12. The configuration in which the front rotor 60 rotates integrally with the rotary shaft 12 is arbitrary. For example, a configuration in which the front rotor 60 is fixed to the rotary shaft 12 or a configuration in which the front rotor 60 is engaged with the outer periphery of the rotary shaft 12. is there.

The front rotor outer peripheral surface 62, which is the outer peripheral surface of the front rotor 60, is a cylindrical surface coaxial with the rotary shaft 12, and the diameter of the front rotor outer peripheral surface 62 is the same as the front cylinder inner peripheral surface 43. However, there may be a slight gap between the front rotor outer peripheral surface 62 and the front cylinder inner peripheral surface 43.

The front rotor 60 has a front rotor surface 70 as a first rotor surface facing the first wall surface 52. The front rotor surface 70 has a ring shape. The front rotor surface 70 includes a first front flat surface 71 and a second front flat surface 72 that are orthogonal to the axial direction Z, and a pair of front curved surfaces 73 that connect both the front

flat surfaces

71 and 72. The first and second front

flat surfaces

71 and 72 correspond to the first and second flat surfaces, respectively.

As shown in FIG. 4, both front

flat surfaces

71 and 72 are displaced in the axial direction Z. The second front flat surface 72 is disposed closer to the first wall surface 52 than the first front flat surface 71. The second front flat surface 72 is in contact with the first wall surface 52. Further, both front

flat surfaces

71 and 72 are separated from each other in the circumferential direction of the front rotor 60 and are shifted by 180 °. Both front

flat surfaces

71 and 72 are fan-shaped. In the following description, the circumferential positions of the

rotors

60 and 80 are referred to as angular positions.

The pair of front curved surfaces 73 are each fan-shaped. As shown in FIG. 3, the pair of front curved surfaces 73 oppose each other in a direction orthogonal to the axial direction Z and the arrangement direction of the front

flat surfaces

71 and 72. Both front curved surfaces 73 have the same shape. The pair of front curved surfaces 73 connect both front

flat surfaces

71 and 72, respectively. One of the pair of front curved surfaces 73 is connected to one end in the circumferential direction of both front

flat surfaces

71 and 72, and the other is connected to the other end in the circumferential direction of both front

flat surfaces

71 and 72. Yes.

As shown in FIG. 3, the angular position of the boundary portion between the front curved surface 73 and the first front flat surface 71 is defined as a first angular position θ1, and the angle of the boundary portion between the front curved surface 73 and the second front flat surface 72 is set. The position is defined as a second angular position θ2. In FIG. 3, each angular position θ1, θ2 is indicated by a broken line, but in reality, the boundary portion is smoothly continuous.

The front curved surface 73 is a curved surface displaced in the axial direction Z according to the angular position of the front rotor 60. The front curved surface 73 is curved in the axial direction Z so as to gradually approach the first wall surface 52 as it goes from the first angular position θ1 to the second angular position θ2. The pair of front curved surfaces 73 are provided on both sides of the second front flat surface 72 in the circumferential direction. The pair of front curved surfaces 73 are curved so as to gradually move away from the first wall surface 52 as they move away from the second front flat surface 72 in the circumferential direction. The front curved surface 73 is not limited to the first angular position θ1 and the second angular position θ2, but the axial direction Z so as to gradually approach or move away from the first wall surface 52 between any two angular positions spaced apart from each other in the circumferential direction. Is curved.

As shown in FIGS. 2 to 4, the rear rotor 80 is ring-shaped and has a rear through hole 81 through which the rotary shaft 12 can be inserted. The rear through hole 81 has the same diameter as the rotary shaft 12. The rear rotor 80 has the rotary shaft 12 inserted through the rear through hole 81 and is engaged with the front rotor 60. The engagement between the front rotor 60 and the rear rotor 80 will be described later. The rear rotor 80 rotates as the rotating shaft 12 rotates. That is, the rear rotor 80 rotates integrally with the rotating shaft 12. The configuration for rotating the rear rotor 80 integrally with the rotary shaft 12 is arbitrary. For example, there is a configuration in which the rear rotor 80 is fixed to the rotary shaft 12 and a configuration in which the rear rotor 80 is engaged with the outer periphery of the rotary shaft 12.

The rear rotor 80 is formed smaller than the front rotor 60. The diameter of the rear rotor 80 is smaller than the diameter of the front rotor 60. A rear rotor outer peripheral surface 82 which is an outer peripheral surface of the rear rotor 80 is a cylindrical surface having a smaller diameter than the front rotor outer peripheral surface 62. The diameter of the rear rotor outer peripheral surface 82 is the same as that of the rear cylinder inner peripheral surface 56. There may be a slight gap between the rear rotor outer peripheral surface 82 and the rear cylinder inner peripheral surface 56.

2 and 4, the rear rotor 80 has a rear rotor surface 90 as a second rotor surface facing the second wall surface 53. The rear rotor surface 90 has a ring shape. The rear rotor surface 90 includes a first rear flat surface 91 and a second rear flat surface 92 that are orthogonal to the axial direction Z, and a pair of rear curved surfaces 93 that connect the rear

flat surfaces

91 and 92. The first and second rear

flat surfaces

91 and 92 correspond to the first and second flat surfaces, respectively.

As shown in FIG. 5, both rear

flat surfaces

91 and 92 are displaced in the axial direction Z. The second rear flat surface 92 is disposed closer to the second wall surface 53 than the first rear flat surface 91. The second rear flat surface 92 is in contact with the second wall surface 53. Both rear

flat surfaces

91 and 92 are separated from each other in the circumferential direction of the rear rotor 80 and are shifted by 180 °. Both rear

flat surfaces

91 and 92 are fan-shaped.

The pair of rear curved surfaces 93 are each fan-shaped. The pair of rear curved surfaces 93 oppose each other in a direction orthogonal to the axial direction Z and the arrangement direction of both rear

flat surfaces

91 and 92. One of the pair of rear curved surfaces 93 connects one end in the circumferential direction of both rear

flat surfaces

91 and 92, and the other end of the other in the circumferential direction of both rear

flat surfaces

91 and 92. Connecting each other.

Both the rotor surfaces 70 and 90 are disposed so as to face the axial direction Z with the intermediate wall portion 51 disposed therebetween. The distance between the two

rotor surfaces

70 and 90 is constant regardless of the angular position and the circumferential position of the two

rotor surfaces

70 and 90. As shown in FIG. 5, the first front flat surface 71 and the second rear flat surface 92 face each other in the axial direction Z, and the second front flat surface 72 and the first rear flat surface 91 face each other in the axial direction Z. Yes. The amount of deviation in the axial direction Z between both front

flat surfaces

71 and 72 is the same as the amount of deviation between both rear

flat surfaces

91 and 92. The amount of deviation in the axial direction Z between the front

flat surfaces

71 and 72 and the amount of deviation between the rear

flat surfaces

91 and 92 are referred to as a deviation amount L1.

As shown in FIG. 4, the bending state of the front curved surface 73 is the same as the curved state of the rear curved surface 93. That is, the front curved surface 73 and the rear curved surface 93 are each curved in the same direction so that the separation distance does not vary according to the angular position. Thereby, the separation distance of both rotor surfaces 70 and 90 is constant at any angular position. Both rotor surfaces 70 and 90 have the same shape except that the diameters are different. Since the shapes of the first rear flat surface 91, the second rear flat surface 92, and the rear curved surface 93 are the same as those of the first front flat surface 71, the second front flat surface 72, and the front curved surface 73, a detailed description will be given. Omitted.

2 to 4, the compressor 10 includes a vane 100 and a vane groove 110 into which the vane 100 is inserted. The vane 100 moves in the axial direction Z as the

rotors

60 and 80 rotate by contacting the

rotors

60 and 80. The vane 100 is disposed between the

rotors

60 and 80, that is, between the rotor surfaces 70 and 90, with the surface of the vane 100 orthogonal to the circumferential direction of the rotating shaft 12. The vane 100 has a plate shape having a thickness in a direction orthogonal to the axial direction Z.

The vane 100 has a first vane end portion 101 and a second vane end portion 102 as both end portions in the axial direction Z. The first vane end portion 101 is in contact with the front rotor surface 70, and the second vane end portion 102 is in contact with the rear rotor surface 90.

As shown in FIG. 2, the vane groove 110 is formed in the rear cylinder 50. The vane groove 110 is formed across both the intermediate wall 51 and the rear cylinder side wall 55. The vane groove 110 is a slit that penetrates the rear cylinder 50 in the radial direction R. Both ends of the vane groove 110 in the radial direction R are open. The vane groove 110 passes through the intermediate wall portion 51. Of the both ends of the vane groove 110 in the axial direction Z, the end on the front rotor 60 side is open. Both side surfaces of the vane groove 110 are opposed to corresponding surfaces of both surfaces of the vane 100. The width of the vane groove 110, that is, the distance between both side surfaces of the vane groove 110 may be equal to or slightly wider than the thickness of the vane 100.

As shown in FIG. 4, the vane groove 110 extends in the axial direction Z from the intermediate wall 51 to the middle of the rear cylinder side wall 55. The vane groove 110 also exists on the radially outer side of the rear rotor 80. The length of the vane groove 110 in the axial direction Z is equal to or longer than the length of the vane 100 in the axial direction Z. Since the vane 100 is inserted into the vane groove 110, the movement of the vane 100 in the circumferential direction is restricted. On the other hand, the vane 100 is allowed to move in the axial direction Z along the vane groove 110.

According to this configuration, when both the

rotors

60 and 80 rotate, the vane 100 moves in the axial direction Z while sliding on both the rotor surfaces 70 and 90. As a result, the first vane end portion 101 of the vane 100 enters the front storage chamber A2, and the second vane end portion 102 enters the rear storage chamber A3. On the other hand, the movement of the vane 100 in the circumferential direction is restricted by contacting the both side surfaces of the vane groove 110. For this reason, even if both

rotors

60 and 80 rotate, the vane 100 does not rotate.

The vane groove 110 allows the vane 100 to be disposed across the two storage chambers A2 and A3, and restricts the rotation of the vane 100 even if both the

rotors

60 and 80 rotate. The moving distance of the vane 100 is the amount of displacement (deviation L1) in the axial direction Z between the front flat surfaces 71 and 72 (or between the rear flat surfaces 91 and 92). The vane 100 is in continuous contact with both rotor surfaces 70 and 90 during the rotation of both

rotors

60 and 80. That is, the vane 100 does not intermittently abut against both the rotor surfaces 70 and 90, and does not repeat separation and contact periodically.

As shown in FIG. 4, a front compression chamber A4 is formed in the front storage chamber A2 by a front rotor 60 (front rotor surface 70), a front cylinder inner peripheral surface 43, and a first wall surface 52.

In the rear housing chamber A3, a rear compression chamber A5 is formed by the rear rotor 80 (rear rotor surface 90), the rear cylinder inner peripheral surface 56, and the second wall surface 53. In both the compression chambers A4 and A5, the volume is periodically changed by the vane 100 as the rotary shaft 12 rotates, and the fluid is sucked / compressed. That is, the vane 100 causes a volume change in both the compression chambers A4 and A5. This point will be described later.

Since the front rotor 60 is formed larger than the rear rotor 80, the front compression chamber A4 is larger than the rear compression chamber A5. That is, the maximum volume of the front compression chamber A4 is larger than the maximum volume of the rear compression chamber A5.

2 and 3, the front rotor 60 is formed with an introduction port 111 for introducing the suction fluid in the motor chamber A1 into the front compression chamber A4. The introduction port 111 has an oval shape that is long in the radial direction R. The shape of the introduction port 111 is not limited to this, and is arbitrary.

The introduction port 111 passes through the front rotor 60 in the axial direction Z. The introduction port 111 is disposed near the outer peripheral end of the front rotor 60. The introduction port 111 communicates with the front compression chamber A4 at a phase where the volume of the front compression chamber A4 increases, and is disposed at a position where it does not communicate with the front compression chamber A4 at a phase where the volume of the front compression chamber A4 decreases.

The introduction port 111 is provided in the vicinity of the boundary between the second front flat surface 72 and the front curved surface 73, specifically, in the vicinity of the circumferential end of the front curved surface 73 near the second front flat surface 72. Further, the introduction port 111 is formed on the front curved surface 73 opposite to the rotation direction with respect to the second front flat surface 72.

As shown in FIGS. 2 and 3, the front cylinder 40 is formed with a communication hole 112 communicating with the introduction port 111. The communication hole 112 is provided at a position corresponding to the introduction port 111. The communication hole 112 is formed at a position overlapping the locus of the introduction port 111 when the front rotor 60 rotates as viewed from the axial direction Z. The communication holes 112 extend in the circumferential direction of the rotating shaft 12, and the four communication holes 112 are separated from each other in the circumferential direction. Thereby, even if the position of the introduction port 111 fluctuates as the front rotor 60 rotates, the communication between the introduction port 111 and the communication hole 112 is easily maintained.

The rear rotor 80 is formed with a discharge port 113 for discharging the compressed fluid compressed in the rear compression chamber A5. The discharge port 113 passes through the rear rotor 80 in the axial direction Z. The discharge port 113 is formed smaller than the introduction port 111. The discharge port 113 is circular. The shape of the discharge port 113 is not limited to this, and is arbitrary.

The discharge port 113 communicates with the rear compression chamber A5 at a phase where the volume of the rear compression chamber A5 decreases, and is disposed at a position where it does not communicate with the rear compression chamber A5 at a phase where the volume of the rear compression chamber A5 increases. The discharge port 113 is provided near the boundary between the second rear flat surface 92 and the rear curved surface 93, specifically, at the circumferential end of the rear curved surface 93 close to the second rear flat surface 92. Further, the discharge port 113 is formed on the rear curved surface 93 on the rotation direction side with respect to the second rear flat surface 92.

When viewed from the axial direction Z, the introduction port 111 is not on the opposite side of the discharge port 113 with respect to a center line passing through the centers of the

rotors

60 and 80 and extending in the direction in which the

flat surfaces

71 and 72 are arranged. It is arranged on the same side as 113. The positions of the introduction port 111 and the discharge port 113 are arbitrary. A discharge valve that closes the discharge port 113 and opens the discharge port 113 based on the application of the specified pressure may be provided. A discharge valve is not essential.

As shown in FIG. 1, the compressor 10 includes a discharge chamber A6 into which the compressed fluid discharged from the discharge port 113 flows, and a discharge flow path 114 that connects the discharge chamber A6 and the discharge port 11b. The discharge chamber A6 is formed by the rear cylinder 50 and the rear housing 22. The discharge chamber A6 is disposed between the discharge port 113 and the rear housing 22. The discharge chamber A6 is formed in a ring shape so as to overlap the locus of the discharge port 113 as the rear rotor 80 rotates as viewed from the axial direction Z. Thereby, according to the angular position of the rear rotor 80, the situation where the discharge port 113 and discharge chamber A6 do not communicate can be suppressed. According to this configuration, the fluid discharged from the discharge port 113 is discharged from the discharge port 11b via the discharge chamber A6 and the discharge flow path 114.

The compressor 10 includes a communication mechanism 120 that switches between a communication state in which both compression chambers A4 and A5 are in communication and a non-communication state in which both compression chambers A4 and A5 are not in communication. A detailed configuration of the communication mechanism 120 will be described below.

As shown in FIGS. 2 to 4, the communication mechanism 120 includes a front boss portion 121 as a first boss portion provided in the front rotor 60, a front rotary valve 122 as a first engagement portion, and a rear rotor 80. A rear boss portion 123 as a second boss portion provided and a rear rotary valve 124 as a second engagement portion are provided.

The front boss 121 protrudes from the front rotor surface 70 toward the rear rotor 80. The front boss portion 121 protrudes toward the rear rotor surface 90 rather than the second front flat surface 72. The front boss portion 121 is formed of a cylinder provided at the inner peripheral end portion of the front rotor surface 70. The rotating shaft 12 is inserted through the front boss portion 121. The outer diameter of the front boss 121 is substantially the same as the diameter of the wall through hole 54. The front boss portion 121 is fitted in a slidable state from the first wall surface 52 to the wall portion through hole 54.

As shown in FIG. 3, the front rotary valve 122 protrudes from the front end surface of the front boss portion 121 toward the rear rotor 80. Two front rotary valves 122 are provided at positions separated in the circumferential direction.

Both front rotary valves 122 are fan-shaped. The inner peripheral surfaces of both front rotary valves 122 are flush with the inner peripheral surface of the front boss portion 121 and are in contact with the outer peripheral surface of the rotating shaft 12. The outer peripheral surfaces of both front rotary valves 122 are flush with the outer peripheral surface of the front boss portion 121.

2 and 4, the rear boss portion 123 protrudes from the rear rotor surface 90 toward the front rotor 60. The rear boss portion 123 protrudes toward the front rotor surface 70 from the second rear flat surface 92. The rear boss portion 123 is formed of a cylinder provided at the inner peripheral end portion of the rear rotor surface 90. The rotating shaft 12 is inserted through the rear boss portion 123. The outer diameter of the rear boss portion 123 is substantially the same as the diameter of the wall portion through hole 54. The rear boss portion 123 is fitted in a slidable state from the second wall surface 53 to the wall portion through hole 54.

The rear rotary valve 124 protrudes from the front end surface of the rear boss portion 123 toward the front rotor 60. The rear rotary valve 124 is a columnar body having a curved inner peripheral surface and outer peripheral surface. The inner peripheral surface of the rear rotary valve 124 is flush with the inner peripheral surface of the rear boss portion 123 and is in contact with the outer peripheral surface of the rotating shaft 12. The outer peripheral surface of the rear rotary valve 124 is flush with the outer peripheral surfaces of both front rotary valves 122. The circumferential length of the rear rotary valve 124 is the same as the circumferential distance between the front rotary valves 122.

5 and 6, the rear rotary valve 124 is engaged with the two front rotary valves 122 in the circumferential direction. The rear rotary valve 124 is fitted between the two rotary valves 122 by being sandwiched between the two front rotary valves 122 from the circumferential direction. When the

rotary valves

122 and 124 are fitted, the relative positions in the circumferential direction of the

rotors

60 and 80 are defined.

The two front rotary valves 122 and the rear rotary valve 124 form a single fan-like connecting valve 125. The connection valve 125 is disposed in the wall through hole 54. Both

rotary valves

122 and 124 are engaged with each other in the wall through hole 54.

The connecting valve 125 is not a closed ring shape but a fan shape. For this reason, an open space 126 in which fluid can move is formed in the wall portion through hole 54. The open space 126 is formed between the rotating shaft 12 and the wall inner peripheral surface 54 a that is the inner peripheral surface of the wall through hole 54. The open space 126 is formed by both end surfaces of the connection valve 125 in the circumferential direction, the outer peripheral surface of the rotating shaft 12, and the wall inner peripheral surface 54a.

The connecting valve 125 has a valve outer peripheral surface 125 a having the same diameter as the wall through hole 54. The valve outer peripheral surface 125 a is configured by the outer peripheral surfaces of both

rotary valves

122 and 124. Since the outer peripheral surfaces of the

rotary valves

122 and 124 are flush with each other, the valve outer peripheral surface 125a becomes one continuous peripheral surface. The valve outer peripheral surface 125 a is in contact with the wall inner peripheral surface 54 a of the wall through hole 54. The wall inner peripheral surface 54a is also an inner peripheral surface of the intermediate wall portion 51 formed in a ring shape.

The communication mechanism 120 includes a communication channel 130 that allows the compression chambers A4 and A5 to communicate with each other. The communication flow path 130 includes a front side opening 131, a rear side opening 132, and a communication groove 133.

As shown in FIG. 5, the front side opening 131 and the rear side opening 132 are formed in the intermediate wall 51. Both

openings

131 and 132 are spaced apart from each other in the circumferential direction of the

rotors

60 and 80. The front side opening 131 and the rear side opening 132 are disposed on both sides of the vane 100. The front opening 131 is on one surface of the vane 100 located on the opposite side of the rotation direction of the

rotors

60 and 80, and the rear opening 132 is a vane located on the rotation direction of the

rotors

60 and 80. It is formed on the other surface of 100, respectively. Both

openings

131 and 132 communicate with the vane groove 110.

As shown in FIG. 3, the front opening 131 opens toward the front compression chamber A4 and the wall through hole 54. The front opening 131 is formed on both the first wall surface 52 and the wall inner peripheral surface 54a of the intermediate wall 51. The front opening 131 is configured to allow the fluid in the front compression chamber A4 to flow into the wall through hole 54.

The front opening 131 is not formed on the second wall surface 53. That is, the front opening 131 does not penetrate the intermediate wall 51 in the axial direction Z, and does not directly communicate with the front compression chamber A4 and the rear compression chamber A5.

As shown in FIG. 2, the rear side opening 132 opens toward the rear compression chamber A5 and the wall through hole 54. The rear side opening 132 is formed on both the second wall surface 53 and the wall portion inner peripheral surface 54 a of the intermediate wall portion 51. The rear opening 132 is configured to allow the fluid in the rear compression chamber A5 to flow into the wall through hole 54. On the other hand, the rear side opening 132 is not formed in the first wall surface 52. That is, the rear side opening 132 does not penetrate the intermediate wall 51 in the axial direction Z, and does not directly connect the front compression chamber A4 and the rear compression chamber A5.

As shown in FIG. 5, the front side opening 131 has a semi-U shape and extends in the radial direction R. The rear side opening 132 has a semi-U shape symmetrical to the front side opening 131. The shape of both opening

parts

131 and 132 is not restricted to this, but is arbitrary. The vane 100 partitions the front side opening 131 and the rear side opening 132. The vane 100 restricts fluid from flowing directly from the front opening 131 toward the rear opening 132.

The communication groove 133 is a portion recessed radially outward from the wall inner peripheral surface 54a. The communication groove 133 is disposed between the front-side opening 131 and the rear-side opening 132 in the wall inner peripheral surface 54 a so as to bypass the vane 100. The communication groove 133 extends in the circumferential direction of the wall inner peripheral surface 54a. The communication groove 133 communicates with the rear side opening 132 and communicates with the open space 126. The circumferential direction of the wall inner peripheral surface 54a coincides with the circumferential direction of both

rotors

60 and 80. For this reason, it can be said that the circumferential direction of the wall inner peripheral surface 54 a is also the circumferential direction of both

rotors

60 and 80.

On the other hand, the communication groove 133 is not in direct communication with the front side opening 131. The communication groove 133 and the front side opening 131 are separated from each other in the circumferential direction of the wall inner peripheral surface 54a. For this reason, the fluid does not flow directly into the communication groove 133 from the front side opening 131. Between the communication groove 133 and the front side opening 131 on the wall inner peripheral surface 54a, the communication groove 133 is not formed, and a grooveless surface 54aa exists.

FIG. 5 shows a case where the connecting valve 125 is disposed on the radially inner side of the front opening 131. In this case, the connection valve 125 closes the opening portion on the radially inner side of the front side opening 131. As a result, the inflow of fluid from the front side opening 131 toward the communication groove 133 is restricted. Therefore, both compression chambers A4 and A5 are in a non-communication state where they are not in communication. In particular, when the connection valve 125 is disposed radially inward with respect to the grooveless surface 54aa, the valve outer peripheral surface 125a of the connection valve 125 is in contact with the grooveless surface 54aa. As a result, fluid leakage from the front opening 131 toward the communication groove 133 is restricted.

FIG. 6 shows a case where the connecting valve 125 moves in the circumferential direction of the

rotors

60 and 80 with respect to the front opening 131. In this case, the connecting valve 125 does not block the opening portion on the radially inner side of the front opening 131. Thereby, the inflow of the fluid from the front side opening 131 toward the communication groove 133 is allowed through the open space 126. Therefore, the fluid in the front compression chamber A4 moves to the rear compression chamber A5 through the front side opening 131 → the open space 126 → the communication groove 133 → the rear side opening 132. Accordingly, a communication state is established in which both compression chambers A4 and A5 are in communication.

The connection valve 125 moves between a closed position that closes the front opening 131 and an open position that opens the front opening 131 according to the angular position of the

rotors

60 and 80. When the connection valve 125 moves to the open position, the front side opening 131 and the communication groove 133 communicate with each other through the open space 126.

In this configuration, the communication period between the front compression chamber A4 and the rear compression chamber A5 in one cycle of rotation of the

rotors

60 and 80 depending on the circumferential length of the valve outer peripheral surface 125a (the angle range occupied by the connecting valve 125). Is defined. The timing at which the two compression chambers A4 and A5 communicate with each other in one rotation period of the

rotors

60 and 80 is defined by the angular position of the connection valve 125. Therefore, by adjusting the angular position of the connecting valve 125 and the circumferential length of the valve outer peripheral surface 125a, the timing and communication period at which the compression chambers A4 and A5 communicate with each other can be adjusted.

As shown in FIGS. 4 and 5, the inner end surface 103, which is the end surface on the radially inner side of the vane 100, is in contact with the outer peripheral surfaces of the

boss portions

121 and 123 and the valve outer peripheral surface 125a. The outer peripheral surfaces of both

boss portions

121 and 123 are flush, the outer peripheral surfaces of both

boss portions

121 and 123 are flush with the valve outer circumferential surface 125a, and the outer circumferential surfaces of both

rotary valves

122 and 124 are flush. The inner end surface 103 of the vane 100 is a concave surface curved with the same curvature as the outer peripheral surfaces of the

boss portions

121 and 123 and the valve outer peripheral surface 125a. Therefore, the inner end surface 103 of the vane 100 is in surface contact with the outer peripheral surfaces of the

boss portions

121 and 123 and the valve outer peripheral surface 125a.

The outer end surface 104 which is the end surface on the radially outer side of the vane 100 is flush with the first part surface 57a of the rear cylinder 50. The outer end surface 104 of the vane 100 is in contact with the front cylinder inner peripheral surface 43 of the front cylinder 40. The vane 100 is sandwiched from the radial direction R by the outer peripheral surfaces of both the

boss portions

121 and 123, the valve outer peripheral surface 125a, and the front cylinder inner peripheral surface 43. Thereby, the position shift of the radial direction R of the vane 100 can be suppressed. Further, a boundary portion between the vane 100 (inner end surface 103) and the outer peripheral surfaces of the

boss portions

121 and 123 and the valve outer peripheral surface 125a, or between the vane 100 (outer end surface 104) and the front cylinder inner peripheral surface 43. The fluid can be prevented from leaking from the boundary portion.

Both

vane end portions

101 and 102 and both

curved surfaces

73 and 93 will be described in detail with reference to FIGS. 7 to 13 in addition to FIGS. 8, FIG. 12, and FIG. 13 schematically show the curvature change and the curve of the contact line.

FIG. 8 is a graph showing the displacement in the axial direction Z of the front rotor surface 70 according to the angular position. The solid line in FIG. 8 indicates the displacement in the axial direction Z of the inner peripheral end of the front rotor surface 70. A one-dot chain line in FIG. 8 indicates the displacement in the axial direction Z of the outer peripheral end of the front rotor surface 70. The vertical axis of the graph in FIG. 8 indicates the amount of displacement in the axial direction Z with respect to the first front flat surface 71. In FIG. 8, the front rotor surface 70 approaches the first wall surface 52 as the displacement in the axial direction Z increases from “0”.

FIG. 8 can also be said to be a graph showing the displacement of the rear rotor surface 90 in the axial direction Z. In this case, the solid line in FIG. 8 indicates the displacement in the axial direction Z of the inner peripheral end of the rear rotor surface 90. A one-dot chain line in FIG. 8 indicates the displacement in the axial direction Z of the outer peripheral end of the rear rotor surface 90. The vertical axis of the graph in FIG. 8 indicates the amount of displacement in the axial direction Z with respect to the first rear flat surface 91. In FIG. 8, the rear rotor surface 90 approaches the second wall surface 53 as the displacement in the axial direction Z increases from “0”.

As shown in FIG. 7, both vane

end portions

101 and 102 have a curved shape that is convex in a direction in which both vane

end portions

101 and 102 are separated from each other. The first vane end portion 101 is curved so as to be convex toward the front rotor surface 70, and the second vane end portion 102 is curved so as to be convex toward the rear rotor surface 90. Both

vane end portions

101 and 102 extend in a vertical direction orthogonal to the axial direction Z and are not inclined in the axial direction Z.

The

vane end portions

101 and 102 are in linear contact with the

curved surfaces

73 and 93 that are curved in the axial direction Z. The contact portions between the

vane end portions

101 and 102 and the

curved surfaces

73 and 93 are shifted in accordance with the degree of bending of the

curved surfaces

73 and 93 with respect to the axial direction Z, specifically, the curvature of the

curved surfaces

73 and 93.

Next, both

curved surfaces

73 and 93 will be described. Hereinafter, the front rotor surface 70 will be described, but the same applies to the rear rotor surface 90.
Both front

flat surfaces

71 and 72 are planes orthogonal to the axial direction Z. For this reason, the inner peripheral end and the outer peripheral end of both front

flat surfaces

71 and 72 are not displaced regardless of the angular position. In FIG. 8, the vicinity of 0 ° corresponds to the second front flat surface 72, and the vicinity of 180 ° corresponds to the first front flat surface 71.

As shown in FIGS. 4 and 8, the front curved surface 73 has a front concave surface 74 that is curved in the axial direction Z so as to be concave toward the first wall surface 52, and a convex toward the first wall surface 52. And a front convex surface 75 that is curved in the axial direction Z.

The front concave surface 74 is disposed closer to the first front flat surface 71 than the second front flat surface 72 and is continuous with the first front flat surface 71. The front convex surface 75 is disposed closer to the second front flat surface 72 than the first front flat surface 71 and is continuous with the second front flat surface 72. The front concave surface 74 is connected to the front convex surface 75. The front curved surface 73 has an inflection point (inflection angle position) θm.

The angle range occupied by the front concave surface 74 is the same as the angle range occupied by the front convex surface 75, and the angular positions of 90 ° and 270 ° respectively correspond to the inflection points θm. Both the angular ranges may be different, and the inflection point θm is not limited to the angular position and is arbitrary.

As shown in FIG. 9, the front concave surface 74 includes a front concave inner peripheral end 74 a and a front concave outer peripheral end 74 b as both ends in the radial direction R. Similarly, the front convex surface 75 includes, as both ends in the radial direction R, a front convex inner peripheral end 75a and a front convex outer peripheral end 75b. Both inner peripheral ends 74a, 75a and both outer peripheral ends 74b, 75b are arcuate.

Both the inner peripheral ends 74 a and 75 a constitute the inner peripheral end of the front curved surface 73. The diameters of both inner peripheral ends 74 a and 75 a are the same as the outer diameter of the front boss portion 121. Both inner peripheral ends 74a and 75a are connected to each other. The front concave inner peripheral end 74 a is connected to the inner peripheral end of the first front flat surface 71, and the front convex inner peripheral end 75 a is connected to the inner peripheral end of the second front flat surface 72. As indicated by the solid line in FIG. 8, the displacement waveform in the axial direction Z of the inner peripheral end of the front rotor surface 70 is a smooth curve.

Both the outer peripheral ends 74 b and 75 b constitute the outer peripheral end of the front curved surface 73. Both outer peripheral ends 74b and 75b are connected to each other. The front concave outer peripheral end 74 b is connected to the outer peripheral end of the first front flat surface 71, and the front convex outer peripheral end 75 b is connected to the outer peripheral end of the second front flat surface 72. As indicated by the one-dot chain line in FIG. 8, the displacement waveform in the axial direction Z of the outer peripheral end of the front rotor surface 70 is a smooth curve.

Here, the curvature indicating the degree of displacement in the axial direction Z according to the angular position is changed between the inner peripheral ends 74a and 75a and the outer peripheral ends 74b and 75b. In the following description, the curvature means the curvature with respect to the axial direction Z, and the curvature radius means the curvature radius of the curvature with respect to the axial direction Z. That is, the curvature and the radius of curvature are parameters indicating the displacement with respect to the axial direction Z. For example, the curvature and the radius of curvature of the arcs of the inner peripheral ends 74a and 75a and the outer peripheral ends 74b and 75b viewed from the axial direction Z are shown. It is not a thing.

Specifically, the curvature radius of the front concave inner peripheral edge 74a is smaller than the curvature radius of the front concave outer peripheral edge 74b. As shown in FIG. 8, the curvature of the displacement curve in the axial direction Z of the front concave inner peripheral edge 74a with respect to the angle change (phase) is smaller than the curvature of the displacement curve in the axial direction Z of the front concave outer peripheral edge 74b with respect to the angular change. . Thereby, in the front concave surface 74, the difference in the axial direction Z between the front concave outer peripheral end 74b and the front concave inner peripheral end 74a gradually increases from the first front flat surface 71 toward the inflection point θm.

Also, the curvature radius of the front convex inner peripheral edge 75a is smaller than the curvature radius of the front convex outer peripheral edge 75b. As shown in FIG. 8, the curvature of the displacement curve in the axial direction Z of the front convex inner peripheral edge 75a with respect to the angle change (phase) is larger than the curvature of the displacement curve in the axial direction Z of the front convex outer peripheral edge 75b with respect to the angular change. . Thereby, in the front convex surface 75, the difference between the front convex surface outer peripheral end 75b and the front convex inner peripheral end 75a is gradually reduced from the inflection point θm toward the second front flat surface 72.

That is, the front curved surface 73 gradually inclines so that the inner peripheral end is farther from the first wall surface 52 than the outer peripheral end as it goes from the first front flat surface 71 to the inflection point θm, and the second curved surface 73 The inner peripheral end and the outer peripheral end are formed so as to approach the same position in the axial direction Z toward the front flat surface 72. That is, at the inflection point θm, which is the boundary portion between the front concave surface 74 and the front convex surface 75, the difference in the axial direction Z between the outer peripheral end and the inner peripheral end of the front curved surface 73 is maximized. On the other hand, at both ends of the front curved surface 73 in the circumferential direction, there is no difference between the outer peripheral end and the inner peripheral end, and both are arranged at the same position in the axial direction Z.

Similarly, as shown in FIGS. 4 and 8, the rear curved surface 93 has a rear concave surface 94 that is curved in the axial direction Z so as to be concave toward the second wall surface 53, and a direction toward the second wall surface 53. And a rear convex surface 95 curved in the axial direction Z so as to be convex. The rear curved surface 93 has an inflection point θm at the same angular position as the front curved surface 73. The rear concave surface 94 is connected to the rear convex surface 95. The front concave surface 74 and the rear convex surface 95 are opposed to each other in the axial direction Z, and the front convex surface 75 and the rear concave surface 94 are opposed to each other in the axial direction Z.

As shown in FIG. 10, the rear concave surface 94 has a rear concave inner peripheral end 94a and a rear concave outer peripheral end 94b. The rear convex surface 95 has a rear convex inner peripheral end 95a connected to the rear concave inner peripheral end 94a and a rear convex outer peripheral end 95b connected to the rear concave outer peripheral end 94b.

The curvature of the rear concave surface 94 and the rear convex surface 95 is the same as the curvature of the front concave surface 74 and the front convex surface 75. The curvature radius of the rear concave inner peripheral edge 94a is smaller than the curvature radius of the rear concave outer peripheral edge 94b, and the curvature radius of the rear convex inner peripheral edge 95a is smaller than the curvature radius of the rear convex outer peripheral edge 95b.

The front concave surface 74 is formed such that the radius of curvature gradually decreases from the front concave outer peripheral end 74b toward the front concave inner peripheral end 74a. The front convex surface 75 is formed such that the radius of curvature gradually decreases from the front convex surface outer peripheral end 75b toward the front convex inner peripheral end 75a. Thereby, the curvature change of the radial direction R in the front concave surface 74 and the front convex surface 75 is continuous.

As shown in FIG. 11, the front curved surface 73 and the rear curved surface 93 are at the inflection point θm (boundary portion between the

concave surfaces

74 and 94 and the convex surfaces 75 and 95) at the inner peripheral end rather than the outer peripheral end. Are inclined in the axial direction Z so as to be separated from the second wall surface 53. When the vane 100 is disposed at an angular position corresponding to the inflection point θm, the first vane end portion 101 abuts both the inner peripheral end and the outer peripheral end of the front curved surface 73, and the second vane end portion 102 abuts both the inner peripheral end and the outer peripheral end of the rear curved surface 93.

In other words, the front curved surface 73 and the rear curved surface 93 are gradually recessed from the outer peripheral end toward the inner peripheral end at least at the inflection point θm, and are directed from the inflection point θm to both angular positions θ1 and θ2. Accordingly, the recess from the outer peripheral end to the inner peripheral end becomes gentle.

A contact manner between the

curved surfaces

73 and 93 configured as described above and the

vane end portions

101 and 102 will be described in detail.
As shown in FIG. 12, the front curved surface 73 is in line contact with the first vane end portion 101. A contact line (contact line) between the front curved surface 73 and the first vane end 101 is referred to as a front contact line (front contact line) P1.

As described above, the first vane end portion 101 extends in the vertical direction orthogonal to the axial direction Z, and the position in the axial direction Z is not displaced. On the other hand, the curvature radius of the front curved surface 73 is different between the inner peripheral end and the outer peripheral end, and is displaced in the axial direction Z between the inner peripheral end and the outer peripheral end at least at the inflection point θm. For this reason, the angular position where the front curved surface 73 contacts the first vane end portion 101 is different between the inner peripheral end and the outer peripheral end of the front curved surface 73. Thereby, the front contact line P1 is not a straight line extending in the radial direction R but a curved line.

Similarly, as shown in FIG. 13, the rear curved surface 93 is in line contact with the second vane end portion 102. A contact line (contact line) between the rear curved surface 93 and the second vane end portion 102 is referred to as a rear contact line (rear contact line) P2.

As described above, the second vane end portion 102 extends in the vertical direction orthogonal to the axial direction Z, and the position in the axial direction Z is not displaced. On the other hand, the curvature radius of the rear curved surface 93 is different between the inner peripheral end and the outer peripheral end, and is displaced in the axial direction Z between the inner peripheral end and the outer peripheral end at least at the inflection point θm. For this reason, as with the front contact line P1, the rear contact line P2 is not a straight line extending in the radial direction R but a curved line.

Here, the vane thickness D, which is the thickness of the vane 100, is such that the

vane end portions

101 and 102 change from the inner peripheral end to the outer peripheral end with respect to the

curved surfaces

73 and 93 regardless of the angular positions of the

curved surfaces

73 and 93. It is set so that it may contact | abut over. Specifically, the vane thickness D is set so that the

vane end portions

101 and 102 come into contact with the inner peripheral ends of the

curved surfaces

73 and 93 when the vane 100 is disposed at an angular position corresponding to the inflection point θm. Is set. The vane thickness D can also be said to be the length of the vane 100 in a direction orthogonal to both the axial direction Z and the longitudinal directions of the

vane end portions

101 and 102. Therefore, the thickness direction of the vane 100 is a direction orthogonal to both the axial direction Z and the longitudinal directions of the

vane end portions

101 and 102.

The curvature radii of the

vane end portions

101 and 102 that are curved so as to be convex toward the rotor surfaces 70 and 90 are such that the

vane end portions

101 and 102 are

curved surfaces

73 and 102 regardless of the angular positions of the

rotors

60 and 80. If it can contact 93 from an inner peripheral end to an outer peripheral end, it is arbitrary. For example, the larger the radius of curvature of the

vane end portions

101 and 102, the greater the difference in the circumferential direction of the contact position between the inner and outer peripheral ends of both

curved surfaces

73 and 93. In consideration of this point, the curvature radius of the

vane end portions

101 and 102 may be larger than the curvature radius when the

vane end portions

101 and 102 are semicircular. Thereby, contact line P1, P2 can be bent more.

When the front curved surface 73 is curved in the axial direction Z so as to approach the first wall surface 52 from the first angular position θ1 toward the second angular position θ2, the rear curved surface 93 facing the front curved surface 73 is It is curved in the axial direction Z so as to be separated from the second wall surface 53 so that the distance from the front curved surface 73 is constant. That is, when either one of the

curved surfaces

73 and 93 is uphill, the other is downhill. Accordingly, when viewed from the axial direction Z, the front contact line P1 is curved in the direction opposite to the rear contact line P2.

The distance between the

curved surfaces

73 and 93 is constant as long as the distance is constant at the same angular position. When the

curved surfaces

73 and 93 have the same shape except that the diameters are different, the distance between the

curved surfaces

73 and 93 at an arbitrary radial position is constant and does not vary depending on the angular position. Become. In addition, the constant separation distance includes some error as long as the

rotors

60 and 80 can rotate within a range where the

vane end portions

101 and 102 and the

curved surfaces

73 and 93 are in contact with each other.

Next, the positional relationship between the introduction port 111, the discharge port 113, and both the

openings

131 and 132, and the compression chambers A4 and A5 will be described in detail with reference to FIGS.
14B is a development view showing both

rotors

60 and 80 and the vane 100 in the state shown in FIG. 14A, and FIG. 15B is a diagram showing both rotors 60 in the state shown in FIG. , 80 and the vane 100. FIGS. 14B and 15B schematically show both

openings

131 and 132 provided in the intermediate wall 51 and the open space 126. The state in which both

openings

131 and 132 are connected via the open space 126 corresponds to the state in which both compression chambers A4 and A5 are in communication.

14A and 14B, when the vane 100 is in contact with the second front flat surface 72 and the first rear flat surface 91, the vane 100 does not enter the front storage chamber A2. In this case, there is one front compression chamber A4, the front compression chamber A4 is filled with suction fluid, and the front compression chamber A4 has a maximum volume.

On the other hand, since a part of the vane 100 has entered the rear housing chamber A3, there are two rear compression chambers A5 (first rear compression chamber A5a and second rear compression chamber) on both sides of the vane 100 in the rear housing chamber A3. A5b) is formed. The first rear compression chamber A5a and the second rear compression chamber A5b are partitioned by the vane 100 and a contact portion between the second rear flat surface 92 and the second wall surface 53, and are adjacent to each other in the circumferential direction.

The first rear compression chamber A5a communicates with the rear side opening 132, but does not communicate with the discharge port 113. The second rear compression chamber A5b communicates with the discharge port 113, but does not communicate with the rear side opening 132. The vane 100 has a first rear compression chamber A5a communicating with the rear side opening 132 and a second rear communicating with the discharge port 113 so that the rear side opening 132 and the discharge port 113 do not directly communicate with each other. Partitions the compression chamber A5b.

Thereafter, when the rotating shaft 12 is rotated by the electric motor 13, both the

rotors

60 and 80 are rotated. Then, the vane 100 moves in the axial direction Z (left and right direction in FIG. 14), and a part of the vane 100 enters the front storage chamber A2. Thereby, as shown in FIG. 15B, two front compression chambers A4 (first front compression chamber A4a and second front compression chamber A4b) are formed on both sides of the vane 100. The first front compression chamber A4a and the second front compression chamber A4b are partitioned by a contact portion between the second front flat surface 72 and the first wall surface 52 and the vane 100, and are adjacent to each other in the circumferential direction.

The first front compression chamber A4a communicates with the introduction port 111 but does not communicate with the front opening 131. The second front compression chamber A4b communicates with the front opening 131, but does not communicate with the introduction port 111. The vane 100 includes a first front compression chamber A4a that communicates with the introduction port 111 and a second front that communicates with the front opening 131 so that the introduction port 111 and the front opening 131 do not directly communicate with each other. The compression chamber A4b is partitioned.

When the

rotors

60 and 80 rotate in this state, the volumes of the compression chambers A4 and A5 change. In the first front compression chamber A4a, the volume increases and the suction fluid is sucked from the introduction port 111, while in the second front compression chamber A4b, the volume decreases and the suction fluid is compressed. Similarly, in the second rear compression chamber A5b, the volume is reduced and the fluid is compressed. On the other hand, in the first rear compression chamber A5a, the space itself is widened, but the fluid does not flow into the first rear compression chamber A5a because the communication mechanism 120 is in a non-communication state.

After that, as shown in FIGS. 15A and 15B, after the vane 100 passes through the first front flat surface 71 and the second rear flat surface 92, both the compression chambers A4 and A5 (the second front compression chamber A4b and the first rear flat surface 92). The compression chamber A5a) communicates. As a result, an intermediate pressure fluid higher in pressure than the suction fluid compressed in the second front compression chamber A4b is introduced into the first rear compression chamber A5a. That is, the communication flow path 130 connects the second front compression chamber A4b and the first rear compression chamber A5a.

After that, when the

rotors

60 and 80 are rotated to a position where the vane 100 contacts the second front flat surface 72 and the first rear flat surface 91, all the intermediate pressure fluid in the second front compression chamber A4b is all in the first rear compression chamber. Introduced into A5a, both compression chambers A4 and A5 are disconnected. On the other hand, the introduced intermediate pressure fluid is compressed as a fluid in the second rear compression chamber A5b when the

next rotors

60 and 80 are rotated, and is discharged from the discharge port 113. In this case, since the intermediate pressure fluid is further compressed in the second rear compression chamber A5b, the compressed fluid having a pressure higher than that of the intermediate pressure fluid is discharged from the discharge port 113.

By rotating both

rotors

60 and 80, in both compression chambers A4 and A5, the suction and compression cycle operations with one cycle of 720 ° (two rotations of both rotors 60 and 80) are repeated. Here, two-stage compression is performed in which the intermediate pressure fluid compressed in the front compression chamber A4 is compressed again in the rear compression chamber A5.

Although the two front compression chambers A4a and A4b have been described separately, paying attention to the fact that a cycle operation with one cycle of 720 ° is performed in the front compression chamber A4, the first front compression chamber A4a has a phase of 0 ° to The 360 ° front compression chamber A4 and the second front compression chamber A4b are front compression chambers A4 having a phase of 360 ° to 720 °. That is, the space formed by the front rotor surface 70, the first wall surface 52, and the inner peripheral surface 43 of the front cylinder is divided by the vane 100 into the front compression chamber A4 having a phase of 0 ° to 360 ° and the phase of 360 ° to 720 °. The front compression chamber A4 is partitioned. In other words, the vane 100 divides the space into a first chamber into which fluid is sucked and a second chamber into which fluid is discharged, and the first chamber and A volume change of the second chamber (increasing the volume of the first chamber and decreasing the volume of the second chamber) is caused. The same applies to the first rear compression chamber A5a and the second rear compression chamber A5b.

The communication flow path 130 is a flow path that connects the front compression chamber A4 having a phase of 360 ° to 720 ° (compression stage) and the rear compression chamber A5 having a phase of 0 ° to 360 ° (suction stage). The communication mechanism 120 communicates or disconnects the front compression chamber A4 having a phase of 360 ° to 720 ° and the rear compression chamber A5 having a phase of 0 ° to 360 °.

Next, the change in volume of both compression chambers A4 and A5 will be described with reference to FIG. In FIG. 16, the broken line indicates the volume change of the front compression chamber A4, the alternate long and short dash line indicates the volume change of the rear compression chamber A5, and the solid line indicates the substantial volume change of both the compression chambers A4 and A5. The total volume change is shown respectively. A phase difference accompanies the volume change of both compression chambers A4 and A5. The phase difference is such that both rotor surfaces 70 and 90 are curved in the axial direction Z so that the distance between them is constant, and the volume of both compression chambers A4 and A5 is changed by one vane 100. Further, the phase difference is realized by connecting the compression chambers A4 and A5 in the latter half of the compression stage of the front compression chamber A4.

As shown in FIG. 16, the volume change of the rear compression chamber A5 is advanced in phase as compared with the volume change of the front compression chamber A4. In the compressor 10, the compression chambers A4 and A5 communicate with each other in the latter half of the compression operation of the suction fluid in the front compression chamber A4, and the suction of the intermediate pressure fluid into the rear compression chamber A5 is started, so that the volume of the rear compression chamber A5 is increased. Is configured to increase. For this reason, as shown by the solid line in FIG. 16, the volume change of the entire compressor 10 is a graph in which the volume change of the front compression chamber A4 and the volume change of the rear compression chamber A5 are connected.

Next, the operation of this embodiment will be described.
As shown in FIGS. 12 and 13, both contact lines P1 and P2 are not straight lines extending in the radial direction R but curved slightly in the circumferential direction. This makes it difficult for the vane 100 to swing in the circumferential direction around at least one of the contact lines P1, P2.

According to the embodiment described above in detail, the following effects are obtained.
(1) The compressor 10 has a rotating shaft 12, a front rotor surface 70 formed in a ring shape, and rotates with the rotation of the rotating shaft 12, and a front rotor outer peripheral surface 62 and a radial direction. And a front cylinder side wall portion 42 having a front cylinder inner circumferential surface 43 facing R and accommodating the front rotor 60. The compressor 10 is inserted into an intermediate wall portion 51 having a first wall surface 52 facing the front rotor surface 70 in the axial direction Z, and a vane groove 110 formed in the intermediate wall portion 51, and as the front rotor 60 rotates. And a vane 100 that moves in the axial direction Z. The compressor 10 is defined by the front rotor surface 70, the first wall surface 52, and the front cylinder inner peripheral surface 43, and the volume is changed by the vane 100 as the front rotor 60 rotates, so that fluid is sucked and compressed. A compression chamber A4 is provided.

The vane 100 has a first vane end portion 101 that is an end portion in the axial direction Z that contacts the front rotor surface 70. The first vane end portion 101 is curved so as to be convex toward the front rotor surface 70, and extends in a direction orthogonal to the axial direction Z. The front rotor surface 70 includes a front curved surface 73 that is displaced and curved in the axial direction Z according to its angular position.

The front curved surface 73 includes a front concave surface 74 that is curved in the axial direction Z so as to be concave toward the first wall surface 52, and a front convex surface 75 that is curved in the axial direction Z so as to be convex toward the first wall surface 52. Including. The front concave surface 74 is formed such that the radius of curvature of the front concave inner peripheral end 74a, which is both ends of the front concave surface 74 in the radial direction R, is smaller than the curvature radius of the front concave outer peripheral end 74b. The front convex surface 75 is formed so that the radius of curvature of the front convex surface inner peripheral end 75a, which is both ends of the front convex surface 75 in the radial direction R, is smaller than the curvature radius of the front convex surface outer peripheral end 75b.

According to this configuration, the front contact line P1, which is the contact position between the first vane end portion 101 and the front rotor surface 70, tends to be curved. This makes it difficult for the vane 100 to swing around the front contact line P1 as compared with the configuration in which the front contact line P1 is linear.

More specifically, as the front rotor 60 rotates, when the first vane end 101 of the non-rotating vane 100 is in contact with the front rotor surface 70, the vane 100 swings about the front contact line P1. There is a fear.

On the other hand, the curvature radius is changed between the front concave inner peripheral edge 74a and the front concave outer peripheral edge 74b so that the front contact line P1 becomes a curve, and the front convex inner peripheral edge 75a and the front convex outer peripheral edge 75b The curvature radius was changed with. Thereby, the attitude | position of the vane 100 is stabilized rather than the case where the front contact line P1 is a straight line, and the vane 100 does not rock easily. Therefore, noise, vibration and fluid leakage due to the swing of the vane 100 can be suppressed.

The fluid leakage due to the oscillation of the vane 100 is, for example, fluid leakage from the boundary portion between the first vane end portion 101 and the front rotor surface 70. Specifically, the first chamber (the first front compression chamber A4a or the second front compression chamber A4b or the suction) is performed from the second chamber (the second front compression chamber A4b or the second rear compression chamber A5b) where the compression is performed via the boundary portion. A fluid leakage into the first rear compression chamber A5a) is conceivable.

(2) The vane 100 is inserted into the vane groove 110. Accordingly, the rotation of the vane 100 in the circumferential direction can be restricted by the contact between the vane 100 and the vane groove 110. Here, the vane 100 is inserted into the vane groove 110 so as to be movable in the axial direction Z. In order to smoothly move the vane 100 in the axial direction Z, a slight gap (clearance) is provided between the vane 100 and the vane groove 110. For this reason, the vane 100 can swing in the vane groove 110. In this regard, according to the present embodiment, the swinging of the vane 100 in the vane groove 110 can be suppressed by making the front contact line P1 curved. Thereby, the swing of the vane 100 in the vane groove 110 can be suppressed while smoothly moving the vane 100 in the axial direction Z.

(3) The vane 100 is a plate having a thickness in a direction orthogonal to both the axial direction Z and the longitudinal direction of the first vane end portion 101. The vane thickness D is set so that the first vane end portion 101 abuts from the inner peripheral end to the outer peripheral end of the front curved surface 73 regardless of the angular position of the front rotor 60. According to this configuration, regardless of the angular position of the front curved surface 73, the state in which the first vane end portion 101 is in contact from the inner peripheral end to the outer peripheral end of the front curved surface 73 is maintained. As a result, a portion where the first vane end portion 101 and the front curved surface 73 do not contact each other is less likely to occur while the front contact line P <b> 1 is a curve. Therefore, it is possible to prevent fluid from leaking from the boundary portion between the first vane end portion 101 and the front curved surface 73.

As already described, the inner peripheral end of the front curved surface 73 is most recessed with respect to the outer peripheral end at the inflection point θm. In view of this point, the vane thickness D is set such that the first vane end portion 101 comes into contact with the inner peripheral end of the front curved surface 73 when the vane 100 is disposed at an angular position corresponding to the inflection point θm. It is good to be set to. As a result, regardless of the angular position of the front rotor 60, the first vane end portion 101 is expected to contact from the inner peripheral end to the outer peripheral end of the front curved surface 73.

(4) The front rotor surface 70 is a first front flat surface 71 that is separated from the first wall surface 52, and a second that is circumferentially separated from the first front flat surface 71 and is in contact with the first wall surface 52. A front flat surface 72. The front curved surface 73 connects both the front

flat surfaces

71 and 72, and is curved in the axial direction Z so as to gradually approach the first wall surface 52 from the first front flat surface 71 toward the second front flat surface 72. is doing. The front concave surface 74 is disposed closer to the first front flat surface 71 than the second front flat surface 72, and the front convex surface 75 is disposed closer to the second front flat surface 72 than the first front flat surface 71. Yes. The front concave surface 74 is connected to the front convex surface 75.

According to this configuration, the difference between the inner peripheral end and the outer peripheral end of the front curved surface 73 is maximized at the boundary portion between the front concave surface 74 and the front convex surface 75, and gradually increases toward both front

flat surfaces

71 and 72. The difference of becomes smaller. Thereby, the connection location (near both angle position (theta) 1, (theta) 2) of the front curved surface 73 and both front

flat surfaces

71 and 72 can be made into a smooth curved surface. Therefore, the front rotor surface 70 and the first vane end 101 can be smoothly slid along with the rotation of the front rotor 60.

(5) In particular, the front compression chamber A4 (first front compression chamber A4a) on the suction side is compressed by the contact portion between the second front flat surface 72 and the first wall surface 52 and the vane 100, and compression is performed. It is possible to partition the front compression chamber A4 (second front compression chamber A4b) to be performed. Thereby, the leakage of the fluid between 1st and 2nd front compression chamber A4a, 4b can be suppressed, and efficiency improves.

(6) The compressor 10 has a rear rotor 80 that rotates with the rotation of the rotary shaft 12, a rear cylinder inner peripheral surface 56 that faces the rear rotor outer peripheral surface 82 in the radial direction R, and accommodates the rear rotor 80. And a rear cylinder side wall 55. The rear rotor 80 has a rear rotor surface 90 that is opposed to the front rotor surface 70 in the axial direction Z and formed in a ring shape. The intermediate wall portion 51 is disposed between the

rotors

60 and 80 and has a second wall surface 53 facing the rear rotor surface 90 in the axial direction Z. The vane 100 has a second vane end 102 that contacts the rear rotor surface 90. The compressor 10 is defined by a rear rotor surface 90, a second wall surface 53, and a rear cylinder inner peripheral surface 56, and a volume change is generated by the vane 100 as the rear rotor 80 rotates, and a fluid is sucked and compressed. A5 is provided.

The rear rotor surface 90 has a rear curved surface 93 including a rear concave surface 94 and a rear convex surface 95 as a second concave surface and a second convex surface. The front concave surface 74 and the rear convex surface 95 are opposed to each other in the axial direction Z, and the front convex surface 75 and the rear concave surface 94 are opposed to each other in the axial direction Z. The curved surfaces 73 and 93 have an inflection point θm at the same angular position, and at least at the inflection point θm, the inner peripheral ends of the

curved surfaces

73 and 93 are inclined so as to be separated from the outer peripheral end. is doing. That is, at least at the inflection point θm, the distance between the inner peripheral ends of the

curved surfaces

73 and 93 is larger than the distance between the outer peripheral ends. When the vane 100 is disposed at an angular position corresponding to the inflection point θm, the

vane end portions

101 and 102 are in contact with the inner peripheral ends of the

curved surfaces

73 and 93.

According to this configuration, the rotation of the

rotors

60 and 80 causes the vane 100 to move in the axial direction Z in a state where both the

vane end portions

101 and 102 are in contact with both the rotor surfaces 70 and 90. Fluid suction and compression are performed at A4 and A5. As a result, fluid can be sucked and compressed in both the compression chambers A4 and A5 without providing the vane 100 corresponding to each of the compression chambers A4 and A5.

Further, according to the present embodiment, the curvature radius of the inner peripheral end of both

concave surfaces

74 and 94 is smaller than the curvature radius of the outer peripheral end, and the curvature radius of the inner peripheral end of both

convex surfaces

75 and 95 is smaller than the curvature radius of the outer peripheral end. Is also getting smaller. Thereby, since both the contact lines P1 and P2 which are contact lines between the

curved surfaces

73 and 93 and the

vane end portions

101 and 102 can be curved, the swing of the vane 100 can be more preferably suppressed. .

Here, by configuring the two

curved surfaces

73 and 93 as described above, at least the inflection point θm, the inner peripheral ends of the two

curved surfaces

73 and 93 are inclined so as to be separated from each other than the outer peripheral end. . In this regard, according to the present embodiment, when the vane 100 is disposed at an angular position corresponding to the inflection point θm, the

vane end portions

101 and 102 are in contact with the inner peripheral ends of the

curved surfaces

73 and 93. . This makes it difficult for a gap to be formed between the

vane end portions

101 and 102 and the

curved surfaces

73 and 93 while making both the contact lines P1 and P2 curved.

(7) The rear rotor surface 90 includes both rear

flat surfaces

91 and 92 disposed at positions shifted in the axial direction Z from each other. The second rear flat surface 92 is in contact with the second wall surface 53. The rear curved surface 93 connects both rear

flat surfaces

91 and 92. The first front flat surface 71 and the second rear flat surface 92 are opposed to each other, and the second front flat surface 72 and the first rear flat surface 91 are opposed to each other. According to this configuration, since the first rear flat surface 91 is disposed at a position facing the second front flat surface 72, the distance between the two is constant, and the movement of the vane 100 is not easily affected. A gap is less likely to occur between the rotor surfaces 70 and 90. The same applies to the rear compression chamber A5.

(8) The front rotor surface 70 includes a second front flat surface 72 as a contact surface in contact with the first wall surface 52. The pair of front curved surfaces 73 are provided on both sides in the circumferential direction of the rotary shaft 12 with respect to the second front flat surface 72. The pair of front curved surfaces 73 are each curved in the axial direction Z so as to gradually move away from the second front flat surface 72 as they move away from the second front flat surface 72 in the circumferential direction. The pair of front curved surfaces 73 are formed such that a front contact line P1 that is a contact line with the first vane end portion 101 is bent in the circumferential direction. That is, the pair of front curved surfaces 73 are formed so that the curvature of the displacement curve in the axial direction Z with respect to the change in angle differs according to the position in the radial direction R. According to this structure, there exists an effect of (1).

The above embodiment may be modified as follows. The above embodiment and each of the following different examples may be combined with each other within a technically consistent range.
The rear rotor 80 may have a larger diameter than the front rotor 60.

Both

rotors

60 and 80 have different diameters, but are not limited to this, and may have the same diameter. That is, the volume of both compression chambers A4 and A5 may be the same.
Both front

flat surfaces

71 and 72 and both rear

flat surfaces

91 and 92 may be omitted. That is, the entire rotor surfaces 70 and 90 may be curved surfaces.

The first vane end portion 101 and the front rotor surface 70 are not limited to a configuration in which the first vane end portion 101 and the front rotor surface 70 are in contact with each other from the inner peripheral end to the outer peripheral end. Further, the first vane end portion 101 and the front rotor surface 70 are not limited to the configuration in which the first vane end portion 101 and the front rotor surface 70 are in contact with each other over the entire circumference, but may be configured to contact over a part of the angle range. The same applies to the second vane end portion 102 and the rear rotor surface 90.

The number of vanes 100 is arbitrary and may be plural, for example. Further, the circumferential position of the vane 100 is arbitrary.
The shapes of the vane 100 and the vane groove 110 are not limited to those of the embodiments as long as the movement of the vane 100 in the axial direction Z is allowed, but the movement in the circumferential direction is restricted. For example, the vane may be fan-shaped.

Further, the vane may be configured to move in the axial direction Z like a pendulum around a predetermined location. That is, the vane is not limited to linear motion, and may be configured to move in the axial direction Z by rotational motion.

The specific shapes of both

cylinders

40 and 50 are arbitrary. For example, the bulging portion 46 may be omitted. Moreover, although both

cylinders

40 and 50 were separate bodies, they may be integrally formed.
Similarly, the specific shapes of the

housings

21 and 22 are also arbitrary.

Both

cylinders

40 and 50 may be omitted. In this case, the inner peripheral surface of the housing 11 may divide both compression chambers A4 and A5. In this configuration, the housing 11 corresponds to a “first cylinder part” and a “second cylinder part”.

The electric motor 13 and the inverter 14 may be omitted. That is, the electric motor 13 and the inverter 14 are not essential in the compressor 10.
Both

rotors

60 and 80 may be fixed to the rotary shaft 12 so as to rotate integrally with the rotary shaft 12, or only one of them is attached to the rotary shaft 12 so as to rotate integrally, and the other is the rotary shaft. The rotary shaft 12 may be attached to the rotary shaft 12 in a rotatable state. Even in this case, since the

rotary valves

122 and 124 are engaged in the circumferential direction, the other rotor rotates as the rotor of the

rotors

60 and 80 rotates.

The outer peripheral surfaces of the

boss portions

121 and 123 are not flush with each other and may be stepped. In this case, the inner end face 103 of the vane 100 is preferably stepped so that no gap is formed.

As shown in FIGS. 17 and 18, the communication mechanism 200 may be formed so as to bypass the intermediate wall portion 51. For example, the communication mechanism 200 may communicate both the compression chambers A4 and A5 via the communication channel 201 formed in both the

cylinder side walls

42 and 55. The communication channel 201 forms a front-side opening formed in a portion of the front cylinder inner peripheral surface 43 that defines the second front compression chamber A4b, and a first rear compression chamber A5a of the rear cylinder inner peripheral surface 56. A rear-side opening in the portion to be connected, and connects the openings. In this case, the communication mechanism 200 switches to a non-communication state when the phase of the front compression chamber A4 is 0 ° to 360 °, and switches to a communication state when the phase of the front compression chamber A4 is 360 ° to 720 °. .

In this case, both

boss portions

121 and 123 and both

rotary valves

122 and 124 may be omitted. That is, it is not essential that the

rotors

60 and 80 are in contact with or engaged with each other.
In this configuration, it is preferable that the wall portion through-hole 54 is reduced in diameter so that the wall portion inner peripheral surface 54a and the rotary shaft 12 are in contact with or close to each other. Further, the inner end surface 103 of the vane 100 may be in direct contact with the rotating shaft 12.

The communication groove 133 may communicate with both the

openings

131 and 132. In this case, the connection valve 125 may have a completely closed ring shape in which the open space 126 is not formed. That is, the

rotary valves

122 and 124 may be formed over the entire circumference in the engaged state. Further, when the communication groove 133 communicates with both of the

openings

131 and 132, the

rotary valves

122 and 124 may be omitted and the

boss tip surfaces

121a and 123a may be in direct contact with each other. That is, the

rotary valves

122 and 124 are not essential. Even in this case, it can be said that the communication mechanism 120 is in a non-communication state when the phase of the front compression chamber A4 is 0 to 360 °, and is switched to a communication state when the phase is 360 ° to 720 °.

As long as both the

rotary valves

122 and 124 are engaged in the circumferential direction, the specific engagement mode is arbitrary. For example, two rear rotary valves 124 are provided, and the front rotary valve 124 is disposed between the front and rear rotary valves 124. A configuration in which the rotary valve 122 is disposed and engaged may be employed.

As long as both the

openings

131 and 132 are spaced apart from each other in the circumferential direction, the specific positions thereof are arbitrary.
The front concave surface 74 and the front convex surface 75, and the rear concave surface 94 and the rear convex surface 95 may be configured to change the curvature only in one of them. That is, it is sufficient that at least one of the contact lines P1, P2 is curved.

Both compression chambers A4 and A5 do not need to communicate. That is, the communication mechanism 120 may be omitted. In this case, the compressor 10 may be configured such that the suction fluid is sucked and the compressed fluid is discharged in each of the compression chambers A4 and A5. For example, a discharge port may be provided in the front rotor 60 and compressed fluid may be discharged from the discharge port, or a suction port may be provided in the rear rotor 80 and suction fluid may be introduced from the suction port.

Either one of the

rotors

60 and 80 may be omitted. For example, as shown in FIG. 19, the front rotor 60 may be omitted. In this case, the front compression chamber A4 is also omitted. That is, two rotors and two compression chambers are not essential.

In this configuration, a suction port 211 may be formed in the intermediate wall portion 51 so that the suction fluid is introduced into the rear compression chamber A5. Further, an urging portion 212 that urges the vane 100 against the rear rotor surface 90 may be provided. According to this configuration, the vane 100 moves in the axial direction Z while sliding on the rear rotor surface 90 as the rear rotor 80 rotates. As a result, a volume change occurs in the rear compression chamber A5, and the suction fluid is sucked and compressed in the rear compression chamber A5.

When the front rotor 60 is omitted, the length of the vane 100 in the radial direction R may be the same as the length of the rear rotor surface 90 in the radial direction R. In this case, the vane groove 110 is formed only in the intermediate wall portion 51 and may not be formed in the rear cylinder side wall portion 55.

In this example, the inner end surface 103 of the vane 100 may be in contact with the rotating shaft 12 (specifically, the outer peripheral surface of the rotating shaft 12). Further, when the front rotor 60 is omitted, the first rear flat surface 91 may be omitted.

20 and 21 show the outer peripheral surface of the inner end surface 103 of the vane 100 curved so as to be concave toward the outer side in the radial direction R and the front boss portion 121 curved so as to be convex toward the outer side in the radial direction R. It shows. As shown in FIGS. 20 and 21, the curvature of the inner end surface 103 of the vane 100 may be smaller than the curvature of the outer peripheral surface of the front boss portion 121. That is, the inner end surface 103 of the vane 100 may be recessed outwardly in the radial direction R and bend more gently than the outer peripheral surface of the front boss portion 121. According to this structure, it can suppress that the curvature of the inner side end surface 103 of the vane 100 becomes larger than the curvature of the outer peripheral surface of the front boss | hub part 121 resulting from a manufacturing error. Thereby, the inconvenience which arises when the curvature of the inner side end surface 103 of the vane 100 becomes larger than the curvature of the outer peripheral surface of the front boss part 121 can be suppressed.

More specifically, if the curvature of the inner end surface 103 of the vane 100 is the same as the curvature of the outer peripheral surface of the front boss portion 121, the curvature of the inner end surface 103 of the vane 100 becomes the same as that of the outer peripheral surface of the front boss portion 121 due to manufacturing errors. Can be greater than curvature. In this case, both ends of the inner end surface 103 of the vane 100 may be caught by the outer peripheral surface of the front boss portion 121, and the vane 100 may not move in the axial direction Z, or both ends of the inner end surface 103 of the vane 100 may be worn. is there.

In this regard, according to this example, even if a manufacturing error or the like occurs by actively curving the inner end surface 103 of the vane 100 more gently than the outer peripheral surface of the front boss portion 121, It is possible to suppress the curvature of the inner end surface 103 of 100 from becoming larger than the curvature of the outer peripheral surface of the front boss portion 121. Thereby, the inconvenience which arises when the curvature of the inner side end surface 103 of the vane 100 becomes larger than the curvature of the outer peripheral surface of the front boss part 121 can be suppressed.

Further, since the inner end surface 103 of the vane 100 is more gently curved than the outer peripheral surface of the front boss portion 121, the second front compression chamber A4b has a contact between the inner end surface 103 of the vane 100 and the outer peripheral surface of the front boss portion 121. There is a gap between them. In the second front compression chamber A4b, the compressed fluid flows between the inner end surface 103 of the vane 100 and the outer peripheral surface of the front boss portion 121. The compressed fluid presses the vane 100 outward in the radial direction R, so that the gap between the outer end surface 104 of the vane 100 and the inner peripheral surface 43 of the front cylinder can be sealed.

Incidentally, the outer peripheral surface of the front boss portion 121 is flush with the outer peripheral surface of the rear boss portion 123. For this reason, it can be said that the curvature of the inner end surface 103 of the vane 100 is smaller than the curvature of the outer peripheral surface of the rear boss portion 123. Similarly, the outer peripheral surfaces of both

boss portions

121 and 123 are flush with the valve outer peripheral surface 125a. For this reason, it can be said that the curvature of the inner end surface 103 of the vane 100 is smaller than the curvature of the valve outer peripheral surface 125a.

Here, both the boss portions 121 and 123 (and the connection valve 125) can be said to be rotor cylinder portions that rotate with the rotation of the rotation shaft 12 in that the rotation shaft 12 is inserted into both the

boss portions

121 and 123. . In this case, it can be said that the curvature of the inner end surface 103 of the vane 100 is smaller than the curvature of the outer peripheral surface of the rotor cylinder portion.

19, when the inner end surface 103 of the vane 100 is brought into contact with the outer peripheral surface of the rotary shaft 12 as in another example, the curvature of the inner end surface 103 of the vane 100 is convex toward the outer side in the radial direction R. It is better that the curvature is smaller than the curvature of the outer peripheral surface of the rotating shaft 12 that is curved.

20 shows the outer end surface 104 of the vane 100 curved so as to be convex outward in the radial direction R and the inner periphery of the front cylinder of the front cylinder 40 curved so as to be convex outward in the radial direction R. A surface 43 is shown. As shown in FIG. 20, the curvature of the outer end surface 104 of the vane 100 may be larger than the curvature of the front cylinder inner peripheral surface 43 of the front cylinder 40. That is, the outer end surface 104 of the vane 100 may be convex outward in the radial direction R and may be curved more than the inner peripheral surface 43 of the front cylinder.
According to this configuration, it is possible to suppress the curvature of the outer end surface 104 of the vane 100 from being smaller than the curvature of the inner peripheral surface 43 of the front cylinder due to a manufacturing error or the like.

More specifically, if the curvature of the outer end surface 104 of the vane 100 and the curvature of the front cylinder inner peripheral surface 43 are the same, the curvature of the outer end surface 104 of the vane 100 is greater than the curvature of the front cylinder inner peripheral surface 43 due to manufacturing errors. Can also be smaller. In this case, both ends of the outer end surface 104 of the vane 100 may be caught by the inner peripheral surface 43 of the front cylinder, and the vane 100 may not easily move in the axial direction Z, or both ends of the outer end surface 104 of the vane 100 may be worn. .

In this respect, according to this example, even if a manufacturing error or the like occurs by actively bending the outer end surface 104 of the vane 100 to be larger than the inner peripheral surface 43 of the front cylinder, It can suppress that the curvature of the outer side end surface 104 becomes smaller than the curvature of the front cylinder internal peripheral surface 43. FIG. Thereby, the inconvenience caused by the curvature of the outer end face 104 of the vane 100 being smaller than the curvature of the front cylinder inner peripheral face 43 can be suppressed.

Further, since the outer end surface 104 of the vane 100 is curved to be larger than the front cylinder inner peripheral surface 43, a gap is formed between the outer end surface 104 of the vane 100 and the front cylinder inner peripheral surface 43 in the second front compression chamber A4b. Occurs. In the second front compression chamber A4b, the compressed fluid flows between the outer end surface 104 of the vane 100 and the front cylinder inner peripheral surface 43. The compressed fluid presses the vane 100 inward in the radial direction R, so that the gap between the inner end surface 103 of the vane 100 and the outer peripheral surface of the front boss portion 121 can be sealed.

The curvature of the inner end surface 103 of the vane 100 may be the same as the curvature of the outer peripheral surface of the front boss portion 121, and the curvature of the outer end surface 104 of the vane 100 may be larger than the curvature of the inner peripheral surface 43 of the front cylinder. Further, the curvature of the inner end face 103 of the vane 100 may be smaller than the curvature of the outer peripheral face of the front boss portion 121, and the curvature of the outer end face 104 of the vane 100 may be the same as the curvature of the front cylinder inner peripheral face 43.

22, on the outer end face 104 of the vane 100, the curvature may be different between the portion disposed in the first front compression chamber A4a and the portion disposed in the second front compression chamber A4b. Specifically, the outer end face 104 of the vane 100 is provided with a first outer end face 221 provided in the first front compression chamber A4a (rotation direction side) and having a curvature larger than that of the front cylinder inner peripheral face 43, and a second front compression face. A second outer end face 222 provided in the chamber A4b (opposite to the rotation direction) and having a larger curvature than the first outer end face 221 may be included. The first outer end surface 221 is closer to the rotation direction than the second outer end surface 222. According to this configuration, in addition to the effects described above, the sealing performance is improved.

More specifically, according to this separate example, the curvature of the first outer end surface 221 is closer to the curvature of the inner peripheral surface 43 of the front cylinder than the curvature of the second outer end surface 222. For this reason, the contact portion between the first outer end surface 221 and the front cylinder inner peripheral surface 43 is easily extended in the circumferential direction, and the contact area between the first outer end surface 221 and the front cylinder inner peripheral surface 43 is increased. Thereby, the sealing performance between the outer end surface 104 of the vane 100 and the inner peripheral surface 43 of the front cylinder is improved.

On the other hand, the second outer end face 222 in the second front compression chamber A4b is curved to be larger than the first outer end face 221. Therefore, in the second front compression chamber A4b, a gap is easily formed between the second outer end surface 222 and the front cylinder inner peripheral surface 43. Thereby, the compressed fluid easily enters between the second outer end face 222 and the front cylinder inner peripheral face 43. Since this compressed fluid presses the vane 100 in the radial direction R, the sealing property between the inner end surface 103 of the vane 100 and the outer peripheral surface of the front boss portion 121 is improved.

The vane 100 may be composed of a plurality of parts. For example, the vane 100 is provided between the vane main body inserted into the vane groove 110 and the vane main body and the front rotor surface 70, and is in contact with the front rotor surface 70. And a tip seal. In this case, the front tip seal or the end of the front tip seal constitutes the end of the vane 100 in the axial direction Z, and corresponds to the “vane end”.

Similarly, the vane 100 may include a rear tip seal that is provided between the vane body and the rear rotor surface 90 and abuts against the rear rotor surface 90. In this case, the rear tip seal or the end of the rear tip seal corresponds to the “vane end”.

The compressor 10 may be used other than the air conditioner. For example, the compressor 10 may be used to supply compressed air to a fuel cell mounted on a fuel cell vehicle.
The mounting target of the compressor 10 is not limited to the vehicle and is arbitrary.

The fluid to be compressed by the compressor 10 is not limited to the refrigerant containing oil, but is arbitrary.

Claims

A rotation axis;
A rotor surface having a rotor shape formed in a ring shape, and rotating with the rotation of the rotating shaft;
A cylindrical portion having an outer peripheral surface of the rotor and an inner peripheral surface facing the radial direction of the rotating shaft, and housing the rotor;
A wall portion having a wall surface facing the rotor surface and the axial direction of the rotation shaft;
A vane inserted into a vane groove formed in the wall and moving in the axial direction as the rotor rotates;
A compression chamber that is partitioned by the rotor surface, the wall surface, and an inner peripheral surface of the cylindrical portion, and in which a volume change is generated by the vane as the rotor rotates, and fluid is sucked and compressed;
The vane has an end in the axial direction and a vane end that contacts the rotor surface;
The vane end portion is curved so as to be convex toward the rotor surface, and extends in a direction perpendicular to the axial direction,
The rotor surface includes a curved surface curved in the axial direction,
The curved surface is curved so as to be displaced in the axial direction according to the angular position,
The curved surface is
A concave surface curved in the axial direction so as to be concave toward the wall surface;
A convex surface curved in the axial direction so as to be convex toward the wall surface,
The concave surface has a concave inner peripheral edge and a concave outer peripheral edge as both ends in the radial direction,
In the concave surface, the radius of curvature of the concave inner peripheral edge in the axial direction is smaller than the radius of curvature of the concave outer peripheral edge,
The convex surface has a convex inner peripheral edge and a convex outer peripheral edge as both ends in the radial direction,
In the convex surface, the curvature radius of the convex inner peripheral edge in the axial direction is smaller than the curvature radius of the convex outer peripheral end.
The compressor according to claim 1,
The vane is a plate having a thickness in a direction orthogonal to both the axial direction and the longitudinal direction of the vane end,
The compressor is configured such that the thickness of the vane is set so that the vane end portion abuts from the inner peripheral end to the outer peripheral end of the curved surface regardless of the angular position of the curved surface.
The compressor according to claim 1 or 2,
The rotor surface has a first flat surface and a second flat surface orthogonal to the axial direction,
The first flat surface is spaced apart from the wall surface in the axial direction;
The second flat surface is provided at a position spaced in the circumferential direction from the first flat surface, abuts on the wall surface,
The curved surface connects the first flat surface and the second flat surface, and bends in the axial direction so as to gradually approach the wall surface from the first flat surface toward the second flat surface. ,
The concave surface is disposed closer to the first flat surface than the second flat surface;
The convex surface is disposed closer to the second flat surface than the first flat surface,
The concave surface is a compressor connected to the convex surface.
The compressor according to any one of claims 1 to 3,
As the rotor, a first rotor and a second rotor that are arranged to face each other in the axial direction;
As the cylindrical portion, a first cylindrical portion having a first inner peripheral surface opposed to the outer peripheral surface of the first rotor in the radial direction and accommodating the first rotor, and an outer peripheral surface of the second rotor And a second cylindrical portion having a second inner peripheral surface facing the radial direction and containing the second rotor,
A first compression chamber and a second compression chamber as the compression chamber;
The first rotor has a first rotor surface as the rotor surface;
The second rotor has a second rotor surface facing the first rotor surface in the axial direction as the rotor surface,
The vane is disposed between the two rotor surfaces, and has a first vane end that contacts the first rotor surface and a second vane end that contacts the second rotor surface as the vane end,
The wall portion is disposed between the first rotor and the second rotor, and as the wall surface, the first wall surface facing the first rotor surface and the axial direction, and the second rotor surface and the axial direction. Having an opposing second wall;
The first compression chamber is defined by the first rotor surface, the first wall surface, and the first inner peripheral surface, and a change in volume is generated by the vane as the first rotor rotates, so that fluid suction and compression are performed. Is a room where
The second compression chamber is defined by the second rotor surface, the second wall surface, and the second inner peripheral surface, and a change in volume is generated by the vane as the second rotor rotates, so that fluid suction and compression are performed. Is a room where
The first rotor surface includes a first curved surface having a first concave surface and a first convex surface connected to each other,
The second rotor surface includes a second curved surface as the curved surface having a second concave surface and a second convex surface connected to each other,
The first concave surface and the second convex surface are opposed in the axial direction;
The first convex surface and the second concave surface are opposed in the axial direction;
The first curved surface and the second curved surface have an inflection point at the same angular position, and at least at the inflection point, the inner peripheral ends of the two curved surfaces are separated from each other than the outer peripheral end. Tilt,
When the vane is disposed at an angular position corresponding to the inflection point, the first vane end is in contact with the inner peripheral end of the first curved surface, and the second vane end is the second A compressor in contact with the inner peripheral end of the curved surface.
The compressor according to any one of claims 1 to 4,
The concave surface is formed such that the radius of curvature in the axial direction gradually decreases from the outer peripheral end of the concave surface toward the inner peripheral end of the concave surface,
The said convex surface is a compressor formed so that the curvature radius of the said axial direction may become small gradually as it goes to the said convex surface inner peripheral end from the said convex surface outer peripheral end.
In the compressor according to any one of claims 1 to 5,
The end surface on the radially inner side of the vane is in contact with the outer peripheral surface of the rotor cylinder portion into which the rotating shaft is inserted and rotated with the rotation of the rotating shaft,
A compressor in which a curvature of a radially inner end face of the vane is smaller than a curvature of an outer peripheral face of the rotor cylinder portion.
In the compressor according to any one of claims 1 to 5,
An end surface on the radially inner side of the vane is in contact with an outer peripheral surface of the rotating shaft,
A compressor in which the curvature of the end surface on the radially inner side of the vane is smaller than the curvature of the outer peripheral surface of the rotating shaft.
The compressor according to any one of claims 1 to 7,
The radially outer end surface of the vane is in contact with the inner peripheral surface of the cylindrical portion,
A compressor in which a curvature of an end face on the radially outer side of the vane is larger than a curvature of an inner peripheral face of the cylindrical portion.
The compressor according to claim 8, wherein
The end surface on the radially outer side of the vane is
A first outer end surface that is disposed on the rotation direction side of the rotation shaft and has a curvature larger than an inner peripheral surface of the cylindrical portion;
A compressor having a second outer end surface disposed on a side opposite to a rotation direction of the rotating shaft and having a curvature larger than that of the first outer end surface.
A rotation axis;
A rotor surface having a rotor shape formed in a ring shape, and rotating with the rotation of the rotating shaft;
A cylindrical portion having an outer peripheral surface of the rotor and an inner peripheral surface facing the radial direction of the rotating shaft, and housing the rotor;
A wall portion having a wall surface facing the rotor surface and the axial direction of the rotation shaft;
A vane inserted into a vane groove formed in the wall and moving in the axial direction as the rotor rotates;
A compression chamber that is partitioned by the rotor surface, the wall surface, and an inner peripheral surface of the cylindrical portion, and in which a volume change is generated by the vane as the rotor rotates, and fluid is sucked and compressed;
The vane has an end in the axial direction and a vane end that contacts the rotor surface;
The vane end portion is curved so as to be convex toward the rotor surface, and extends in a direction perpendicular to the axial direction,
The rotor surface includes a curved surface curved in the axial direction,
The curved surface is curved so as to be displaced in the axial direction according to the angular position,
The curved surface includes a portion having a radius of curvature different from the axial direction according to the radial position so that at least a part of a contact line between the curved surface and the vane end portion bends in a circumferential direction of the rotor. Including compressor.