JP2019178669A - Compressor - Google Patents

Abstract

To provide a compressor capable of suitably performing compression of fluid using two compression chambers.SOLUTION: A compressor 10 includes two rotors 60, 80 opposed to each other in an axial direction Z, and a vane 100 abutting on both the rotors 60, 80. The vane 100 is moved in the axial direction Z with the rotation of both the rotors 60, 80 while being restricted not to be rotated by a vane groove. Herein, the compressor 10 further includes compression chambers A4, A5 where the suction and compression of fluid are performed along with the rotation of the rotors 60, 80, and a communication mechanism 120 for switching between a communication state that both the compression chambers A4, A5 are communicated and a non-communication state that both the compression chambers A4, A5 are not communicated.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor.

  For example, Patent Document 1 discloses a compressor that includes a rotation shaft, a rotor that rotates as the rotation shaft rotates, a vane that moves in the axial direction of the rotation shaft as the rotor rotates, and a compression chamber. Are listed. In the compressor, as the rotor rotates, fluid is sucked and compressed in the compression chamber. Patent Document 1 describes that two compression chambers are provided corresponding to two rotors, and that fluid is sucked and compressed independently in each of the compression chambers.

JP 51-97006 A

  Here, there is still room for improvement in the compressor in which the suction and compression of the fluid are performed in the two compression chambers while the vane moves in the axial direction of the rotation shaft by the rotation of the rotor as described above. .

  This invention is made | formed in view of the situation mentioned above, The objective is to provide the compressor which can compress a fluid suitably using two compression chambers.

  A compressor that achieves the above object has a rotary shaft, a ring-shaped first rotor surface, and rotates in accordance with the rotation of the rotary shaft, and the axial direction of the first rotor and the rotary shaft And a second rotor having a ring-shaped second rotor surface, and an outer peripheral surface of the first rotor and a radial direction of the rotation shaft. A first cylindrical portion that houses the first rotor, a second inner circumferential surface that faces the outer circumferential surface of the second rotor in the radial direction, and A second cylindrical portion that accommodates two rotors, and a first wall surface that faces the first rotor surface in the axial direction and a second wall surface that faces the first rotor surface in the axial direction. A wall portion having a second wall surface, and both the rotors inserted in a vane groove formed in the wall portion; The vane moves in the axial direction as the rotors rotate, and the first rotor surface, the first wall surface, and the first inner peripheral surface define the rotation of the first rotor. And the second rotor surface, the second rotor surface, the second wall surface, and the second inner peripheral surface, and is divided by the first compression chamber in which the volume is changed by the vane and the fluid is sucked and compressed. The first compression chamber and the second compression chamber are in communication with each other, the second compression chamber in which the volume is changed by the vane with rotation of the vane and the fluid is sucked and compressed, and the first compression chamber and the first compression chamber are in communication with each other. And a communication mechanism that switches to a non-communication state in which the compression chamber and the second compression chamber are not in communication with each other.

  According to this configuration, when both rotors rotate, the volume is changed by the vanes, and fluid is sucked and compressed in both compression chambers. Moreover, according to this structure, both the compression chambers can be communicated or can not be communicated by the communication mechanism. As a result, for example, the fluid compressed in the first compression chamber can flow into the second compression chamber and be compressed again, or the fluid in both the compression chambers can be compressed while both the compression chambers communicate with each other. Can be. Therefore, the fluid can be compressed with a high degree of freedom using the two compression chambers. Therefore, the fluid can be suitably compressed using the two compression chambers.

  About the compressor, the wall portion is formed with a wall portion through hole penetrating in the axial direction, and the wall portion through hole is formed larger in the radial direction than the rotating shaft, The communication mechanism includes a communication flow path for communicating the first compression chamber and the second compression chamber via the rotation shaft and the inner peripheral surface of the wall through hole, and the angular positions of the two rotors. Accordingly, a valve that moves to an open position for opening the communication flow path and a closed position for closing the communication flow path may be provided.

  According to such a configuration, the valve moves between the open position and the closed position as both the rotors rotate, so that it can be in a communication state or a non-communication state depending on the angular position.

  In particular, according to this configuration, since the communication flow path communicates between the rotation shaft and the inner peripheral surface of the wall through hole, for example, radially outside of both rotors so as to bypass the wall. Compared with the configuration in which the communication flow path is provided in the compressor, it is possible to suppress the enlargement of the compressor in the radial direction.

  With respect to the compressor, the communication channel is formed in a communication groove that is recessed from the inner peripheral surface of the wall portion through-hole to the radially outer side of the rotation shaft, and in the wall portion, and the first compression chamber and the wall The first opening that opens toward the through-hole and the first opening in the wall are formed at different positions in the circumferential direction, and open toward the second compression chamber and the wall through-hole. The valve has a fan shape and is disposed in the wall through hole, and the valve has a valve outer peripheral surface in contact with an inner peripheral surface of the wall through hole. And the communication groove communicates with one of the openings, but is separated from the other opening, and the valve is disposed in the closed position. The opening portion in which the valve opens toward the wall through hole in the other opening When the valve is disposed at the radially inner side, the opening is closed by the outer peripheral surface of the valve, and the valve is disposed at the open position, the valve is circumferential with respect to the opening. The fluid is allowed to move from the first compression chamber to the second compression chamber through an open space that is disposed at a shifted position and is formed in the wall through hole and communicates with the communication groove. Good.

  According to such a configuration, the valve moves between the open position and the closed position while both rotors rotate once. As a result, the two compression chambers can be communicated or non-communication while both rotors rotate once.

  In particular, according to this configuration, it is possible to adjust the period during which the two compression chambers communicate with each other by adjusting the circumferential length of the valve outer peripheral surface. Further, the timing at which both compression chambers communicate can be adjusted by adjusting the angular position of the valve. Thereby, the communication / non-communication adjustment of both compression chambers can be easily and freely performed.

  In the compressor, the communication mechanism includes a cylindrical first boss projecting from the inner peripheral end of the first rotor surface toward the second rotor, and an inner peripheral end of the second rotor surface. A cylindrical second boss portion protruding toward the first rotor, and the valve includes a first engagement portion protruding toward the second rotor from a tip surface of the first boss portion; A second engaging portion that protrudes from the front end surface of the second boss portion toward the first rotor and engages with the first engaging portion in the circumferential direction; and It is good to be comprised by the outer peripheral surface of the said both engaging parts.

  According to such a configuration, both rotors are engaged in the circumferential direction by the both engaging portions constituting the valve that switches between the communication state and the non-communication state. Thereby, since the relative position of both rotors in the circumferential direction of both rotors is defined, it is possible to suppress displacement of both rotors in the circumferential direction of both rotors.

  In particular, since both engaging portions are engaged in the circumferential direction, the relative position is not likely to fluctuate due to the engagement of both engaging portions even when both rotors are rotating. Thereby, the fluctuation | variation of the said relative position during rotation of both rotors can be suppressed. In addition, the rotational force of one of the rotors is transmitted to the other through the engaging portions of both engaging portions. Thereby, the synchronization of rotation of both rotors can be improved.

  In the compressor, the vane has a first vane end portion and a second vane end portion that are both end portions in the axial direction, and the first rotor surface with which the first vane end portion abuts is, The first rotor surface that is displaced in the axial direction according to the angular position, and the second rotor surface with which the second vane end is in contact is arranged in the axial direction according to the angular position. The first curved surface and the second curved surface are opposed to each other in the axial direction, and the facing distance is constant regardless of the angular position. It may be curved in the axial direction.

  According to such a configuration, when both rotors rotate, the vane moves along both curved surfaces, so that it naturally moves in the axial direction. Thereby, it is not necessary to separately provide a configuration for moving the vanes, and the configuration can be simplified.

  According to this invention, fluid compression can be suitably performed using two compression chambers.

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. Sectional drawing of both rotors, vanes, and a rear cylinder. FIG. 6 is a sectional view taken along line 6-6 of FIG. The bottom view of the main structures in the state where both cylinders are partially broken. FIG. 8 is a cross-sectional view taken along line 8-8 in FIG. 4 in a non-communication state. FIG. 8 is a cross-sectional view taken along line 8-8 in FIG. 4 in a communication state. (A) Sectional drawing which shows both rotors and its periphery, (b) The developed view which shows the state of both rotors and vanes in the state of (a). (A) Sectional drawing which shows both rotors and its periphery, (b) The developed view which shows the state of both rotors and vanes in the state of (a). The graph which shows the volume change of 1st Embodiment. Sectional drawing which shows the outline | summary of the compressor of 2nd Embodiment typically. Sectional drawing for demonstrating the communication mechanism of 2nd Embodiment. The expanded view which shows the mode of both rotors and vanes. The expanded view which shows the mode of both rotors and vanes. (A) The graph which shows the volume change etc. of 2nd Embodiment, (b) The time chart which shows the state of an opening-and-closing part, (c) The time chart which shows the state of a communication mechanism. The schematic diagram which shows another example of a communication mechanism. The schematic diagram which shows another example of a communication mechanism.

(First embodiment)
Hereinafter, a first embodiment of a compressor will be described with reference to FIGS. In addition, the compressor of this embodiment is for vehicles, for example, and is mounted on the vehicle and used in detail. The compressor is used in, for example, a vehicle air conditioner, and the fluid to be compressed by the compressor is a refrigerant containing oil. For convenience of illustration, in FIG. 1 and FIG. 4 and the like, the rotary shaft 12 and both rotors 60 and 80 are shown in side views.

  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, and a rear rotor 80. ing.

  The housing 11 has, for example, a cylindrical shape as a whole, and includes 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, for example, at a position on the bottom side of the opening end portion in the side wall portion of the front housing 21. However, 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. However, the position of the discharge port 11b is arbitrary.

The front housing 21 and the rear housing 22 are unitized with the openings facing each other.
The inverter cover 23 is disposed on the opposite side of the front housing 21 from the rear housing 22 side. 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.

An 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. Specifically, a ring-shaped first bearing holding portion 31 protruding from the bottom portion is provided at the bottom portion of the front housing 21, and on the inner side in the radial direction R of the rotary shaft 12 with respect to the first bearing holding portion 31. The 1st radial bearing 32 which supports the 1st end part of the rotating shaft 12 rotatably is provided. Similarly, a ring-shaped second bearing holding portion 33 projecting from the bottom portion is provided at the bottom portion of the rear housing 22, and the first end portion of the rotating shaft 12 and the second bearing holding portion 33 are disposed inside the second bearing holding portion 33. Is provided with a second radial bearing 34 for rotatably supporting the second end portion on the opposite side. 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 accommodates 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 includes a front cylinder bottom portion 41 and a front cylinder side wall portion 42 erected from the front cylinder bottom portion 41 toward the rear housing 22. The front cylinder side wall portion 42 enters the inside of the rear housing 22.

  As shown in FIGS. 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, for example, a cylindrical surface extending in the axial direction Z. The front cylinder 40 has a front enlarged surface 44 having a diameter larger than that of the front cylinder inner peripheral 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 projecting outward in the radial direction R of the rotary shaft 12. The bulging portion 46 is provided at a position on the base end side (front cylinder bottom 41 side) of the front cylinder side wall portion 42. The front housing 21 and the rear housing 22 are unitized with the bulging portion 46 interposed therebetween. The positional deviation in the axial direction Z of the front cylinder 40 is regulated by both the housings 21 and 22.

  As shown in FIG. 4, the front cylinder bottom 41 has a step shape in the axial direction Z, and a first bottom 41a disposed on the center side, and the radial direction of the rotary shaft 12 with respect to the first bottom 41a. And a second bottom portion 41b disposed on the rear housing 22 side of the first bottom portion 41a. 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, in this embodiment, the motor chamber A1 is defined by the front housing 21 and the front cylinder bottom 41, 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 supplied with driving power from the inverter 14.

  Incidentally, since the suction port 11a is provided in the front housing 21 that partitions the motor chamber A1, 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 of the present embodiment, the inverter 14, the electric motor 13, and both the rotors 60 and 80 are arranged in order in the axial direction Z. However, the position of each of these components is arbitrary, and for example, the inverter 14 may be disposed outside the radial direction R of the rotating shaft 12 with respect to the electric motor 13.

  As shown in FIGS. 2 to 4, the rear cylinder 50 has a bottomed cylindrical shape that opens 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 being abutted against the bottom of the rear housing 22.

  The rear cylinder 50 includes an intermediate wall portion 51 that constitutes a bottom portion of the rear cylinder 50, and a rear cylinder side wall portion 55 that stands in the axial direction Z from the intermediate wall portion 51 toward the rear housing 22. The intermediate wall portion 51 corresponds to a “wall portion”.

  As shown in FIG. 4, the intermediate wall portion 51 is disposed such that the wall thickness direction coincides with the axial direction Z, and has a first wall surface 52 and a second wall surface 53 that are orthogonal to the axial direction Z. . The intermediate wall 51 has a ring shape (in detail, an annular 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 through hole 54 is formed larger than the rotating shaft 12. That is, the wall 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 (in detail, a cylindrical shape) extending in the axial direction Z, and includes a rear cylinder inner peripheral surface 56 as a second inner peripheral surface and a rear cylinder outer peripheral surface 57. ing.
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 inner side in the radial direction R of the rotary shaft 12 with respect to the front cylinder inner peripheral surface 43.

  The rear cylinder outer peripheral surface 57 is composed of a plurality of cylindrical surfaces having different diameters, and has a stepped shape. Specifically, the rear cylinder outer peripheral surface 57 includes a first part surface 57a, a second part surface 57b having a diameter larger than the first part surface 57a, and a third part having a diameter larger than the second part surface 57b. Surface 57c.

  The first part surface 57 a is in contact with the front cylinder inner peripheral surface 43. The second part surface 57b is in contact with the front enlarged diameter surface 44. The third part surface 57 c 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 is in contact with the front step surface 45, and the second rear step surface 59 formed between the two part surfaces 57b and 57c is the front surface. It is in contact with the open end of the cylinder 40.

  Here, as shown in FIG. 4, a front storage chamber A <b> 2 that stores the front rotor 60 is formed by the front cylinder bottom 41, the front cylinder inner peripheral surface 43, and the first wall surface 52. The front storage chamber A2 is formed in a columnar shape as a whole.

  Similarly, 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 is formed in a columnar shape as a whole.

  In the present embodiment, the rear storage chamber A3 is formed smaller than the front storage chamber A2. Specifically, the diameter of the rear cylinder inner peripheral surface 56 is smaller than the diameter of the front cylinder inner peripheral surface 43. For this reason, the rear storage chamber A3 is smaller than the front storage chamber A2, and the volume of the rear storage chamber A3 is smaller than the volume of the front storage chamber A2.

  Both storage chambers A2 and A3 are partitioned by an intermediate wall portion 51, and both rotors 60 and 80 are disposed to face each other in the axial direction Z via the intermediate wall portion 51. That is, the intermediate wall portion 51 is disposed between the rotors 60 and 80.

Incidentally, the rotating shaft 12 and both rotors 60 and 80 are the same shaft. That is, the compressor 10 has a structure of an axial movement, not an eccentric movement.
Here, the circumferential direction of both the rotors 60 and 80 and the circumferential direction of the rotating shaft 12 coincide, and the radial direction of both the rotors 60 and 80 and the radial direction R of the rotating shaft 12 coincide with each other. The axial directions 60 and 80 coincide with the axial direction Z of the rotary shaft 12. 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 5, the front rotor 60 has a ring shape (for example, an annular shape) and includes a front through hole 61 into which the rotating 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 is configured to rotate with the rotation of the rotating shaft 12. That is, the front rotor 60 and the rotating shaft 12 rotate integrally. The specific configuration for integrally rotating the front rotor 60 and the rotating shaft 12 is arbitrary. For example, the front rotor 60 is fixed to the rotating shaft 12 or the front rotor 60 is connected to the rotating shaft 12. On the other hand, the structure etc. which are engaged in the circumferential direction can be considered.

  A front rotor outer peripheral surface 62, which is an outer peripheral surface of the front rotor 60, is a cylindrical surface that is coaxial with the rotary shaft 12 and has the same diameter 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, and specifically has an annular shape. The front rotor surface 70 includes a first front flat surface 71 and a second front flat surface 72 orthogonal to the axial direction Z, and a pair of front curved surfaces 73 as curved surfaces connecting the two front flat surfaces 71 and 72. ing.

  As shown in FIG. 5, both front flat surfaces 71 and 72 are shifted in the axial direction Z. Specifically, the second front flat surface 72 is disposed at a position 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. Moreover, both the front flat surfaces 71 and 72 are spaced apart from each other in the circumferential direction of the front rotor 60, and for example, both are shifted by 180 °. In this embodiment, both front flat surfaces 71 and 72 are fan-shaped. In the following description, the circumferential positions of the rotors 60 and 80 are also referred to as angular positions.

  Each of the pair of front curved surfaces 73 has a fan shape. As shown in FIG. 3, the pair of front curved surfaces 73 are disposed to face each other in a direction orthogonal to both the axial direction Z and the opposed directions 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. Specifically, one of the pair of front curved surfaces 73 connects one end of the front flat surfaces 71, 72 in the circumferential direction, and the other is the one end of the front flat surfaces 71, 72 in the circumferential direction. The other end parts on the opposite side to the part are connected to each other.

  Here, for convenience of explanation, 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 front curved surface 73 and the second front flat surface. The angular position of the boundary portion with 72 is defined as a second angular position θ2. For convenience of illustration, in FIG. 3, the angular positions θ1 and θ2 are indicated by broken lines, but in reality, the boundary portions are 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. Specifically, the front curved surface 73 is curved in the axial direction Z so as to gradually approach the first wall surface 52 from the first angular position θ1 toward the second angular position θ2. Therefore, as shown in FIG. 6, when the front curved surface 73 is cut in the middle of the front curved surface 73, the front curved surface 73 is between the front flat surfaces 71 and 72 in the axial direction Z, and is the first wall surface. It is in a position separated from 52.

  However, the front curved surface 73 of the present embodiment is not limited to the first angular position θ1 and the second angular position θ2, and gradually approaches the first wall surface 52 between any two angular positions spaced apart from each other in the circumferential direction ( Or curved away in the axial direction Z.

  In the present embodiment, as shown in FIG. 7, the front curved surface 73 is directed toward the first wall surface 52 and the front concave surface 73 a curved in the axial direction Z so as to be concave toward the first wall surface 52. And a front convex surface 73b curved in the axial direction Z so as to be convex.

  The front concave surface 73a is disposed closer to the first front flat surface 71 than the second front flat surface 72, and the front convex surface 73b is disposed closer to the second front flat surface 72 than the first front flat surface 71. Yes. The front concave surface 73a and the front convex surface 73b are connected. That is, the front curved surface 73 is a curved surface having an inflection point.

The angle range occupied by the front convex surface 73b and the angle range occupied by the front concave surface 73a may be the same or different. The position of the inflection point is arbitrary.
As shown in FIGS. 2 to 5, the rear rotor 80 has a ring shape (for example, an annular shape) 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 is configured to rotate with the rotation of the rotating shaft 12. That is, the rear rotor 80 and the rotating shaft 12 rotate integrally. The specific configuration for integrally rotating the rear rotor 80 and the rotary shaft 12 is arbitrary. For example, a configuration in which the rear rotor 80 is fixed to the rotary shaft 12 or a configuration in which the rear rotor 80 rotates around the rotary shaft 12. The structure etc. which are engaged in the direction may be sufficient.

  In the present embodiment, as shown in FIGS. 4 to 6, the rear rotor 80 is formed smaller than the front rotor 60. Specifically, 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. However, there may be a slight gap between the rear rotor outer peripheral surface 82 and the rear cylinder inner peripheral surface 56.

  As shown in FIGS. 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, and specifically has an annular 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 as curved surfaces that connect the two rear flat surfaces 91 and 92. Yes.

  As shown in FIG. 5, both rear flat surfaces 91 and 92 are shifted in the axial direction Z. Specifically, the second rear flat surface 92 is disposed at a position 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. Moreover, both the rear flat surfaces 91 and 92 are spaced apart from each other in the circumferential direction of the rear rotor 80, and for example, both are shifted by 180 °. In the present embodiment, both rear flat surfaces 91 and 92 are fan-shaped.

Each of the pair of rear curved surfaces 93 has a fan shape. The pair of rear curved surfaces 93 are arranged to face each other in a direction orthogonal to both the axial direction Z and the opposing directions of the 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 is opposite to the one end in the circumferential direction of both rear flat surfaces 91 and 92. The other ends on the side are connected.

  Both rotor surfaces 70 and 90 are opposed to each other in the axial direction Z with the intermediate wall portion 51 interposed therebetween. The facing distance between the rotor surfaces 70 and 90 is constant regardless of the angular position (in other words, the circumferential position).

  Specifically, as shown in FIG. 5, the first front flat surface 71 and the second rear flat surface 92 are opposed to each other in the axial direction Z, and the second front flat surface 72 and the first rear flat surface 91 are Opposite the axial direction Z. 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 the same. Hereinafter, the shift amount in the axial direction Z between the front flat surfaces 71 and 72 and the shift amount between the rear flat surfaces 91 and 92 are simply referred to as a shift amount L1.

  As shown in FIGS. 4, 6, and 7, the degree of bending of the front curved surface 73 and the degree of bending of the rear curved surface 93 are the same. That is, the front curved surface 73 and the rear curved surface 93 are curved in the same direction so that the facing distance does not vary according to the angular position. Thereby, the opposing distance between both rotor surfaces 70 and 90 is constant at any angular position.

  In the present embodiment, both rotor surfaces 70 and 90 have the same shape except that the diameters are different. The specific shapes of the first rear flat surface 91, the second rear flat surface 92, and the rear curved surface 93 are the same as the first front flat surface 71, the second front flat surface 72, and the front curved surface 73. Detailed description is omitted.

  As shown in FIGS. 2 to 5, the compressor 10 includes a vane 100 that contacts the rotors 60 and 80 and moves in the axial direction Z as the rotors 60 and 80 rotate, and the vane 100 is inserted. Vane groove 110.

  The vane 100 has a plate shape, for example. The vane 100 is disposed between the rotors 60 and 80 (in other words, both rotor surfaces 70 and 90) so that the plate surface of the vane 100 is orthogonal to the circumferential direction of the rotating shaft 12, for example. In other words, the vane 100 has a plate shape in which the thickness direction is a direction orthogonal to the axial direction Z (in other words, a tangential direction of the outer peripheral surfaces 62 and 82 of both rotors).

  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. In addition, although the specific shape of both the vane edge parts 101 and 102 is arbitrary, it is good to be curved so that it may become convex toward both rotor surfaces 70 and 90, for example.

  As shown in FIGS. 2 to 4, the vane groove 110 is formed in the rear cylinder 50, for example. Specifically, the vane groove 110 is formed across both the intermediate wall portion 51 and the rear cylinder side wall portion 55. In the present embodiment, 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. Further, the vane groove 110 passes through the intermediate wall portion 51, and the end portion on the front rotor 60 side of both end portions in the axial direction Z of the vane groove 110 is open. The vane groove 110 has both side surfaces opposed to each other in the circumferential direction. Both side surfaces of the vane groove 110 and both plate surfaces of the vane 100 face each other. The width of the vane groove 110 (in other words, the opposing distance between both side surfaces of the vane groove 110) may be the same as or slightly larger than the plate thickness of the vane 100.

  As shown in FIGS. 4 and 7, the vane groove 110 extends in the axial direction Z from the intermediate wall portion 51 to a middle position of the rear cylinder side wall portion 55. The vane groove 110 also exists outside the rear rotor 80 in the radial direction R. The length of the vane groove 110 in the axial direction Z may be the same as or longer than the length of the vane 100 in the axial direction Z. The movement of the vane 100 in the circumferential direction is restricted by being inserted into the vane groove 110 (in detail, pinched). On the other hand, the vane 100 is allowed to move in the axial direction Z along the vane groove 110.

  According to such a configuration, the vanes 100 move in the axial direction Z along the both rotor surfaces 70 and 90 by rotating both the rotors 60 and 80. As a result, the first vane end 101 of the vane 100 enters the front storage chamber A2, and the second vane end 102 enters the rear storage chamber A3.

  On the other hand, since the vane 100 is restricted from moving in the circumferential direction by abutting against the vane groove 110 (specifically, both side surfaces of the vane groove 110 facing each other), the rotation of the rotors 60 and 80 is prevented. Accordingly, the vane 100 is prevented from rotating.

  In other words, 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 accompanying the rotation of the rotors 60 and 80. It can be said that there is.

  The moving distance of the vane 100 is a displacement amount (deviation amount L1) in the axial direction Z between the front flat surfaces 71 and 72 (or between the rear flat surfaces 91 and 92). Further, the vane 100 maintains a state where it is in contact with both the rotor surfaces 70 and 90 while the both rotors 60 and 80 are rotating. That is, the vane 100 is continuously in contact with the rotor surfaces 70 and 90 during the rotation of the rotors 60 and 80, and is intermittently contacted (specifically, the vane 100 is periodically separated or contacted). ) Will not occur.

  In the present embodiment, as shown in FIG. 6, the curved surfaces 73 and 93 are slightly recessed from the outer side in the radial direction R toward the inner side in the radial direction R within the range where they are in contact with the vane end portions 101 and 102. It may be inclined. In this case, both vane end portions 101 and 102 are in contact with both curved surfaces 73 and 93 from the inner peripheral end to the outer peripheral end while the contact portions are slightly shifted in the circumferential direction. However, the present invention is not limited to this, and both curved surfaces 73 and 93 may be configured to extend straight in a direction orthogonal to the axial direction Z so that displacement in the radial direction R does not occur at the same angular position. That is, the opposing distances of the curved surfaces 73 and 93 may be slightly changed according to the radial direction R as long as the opposing distance is constant at the angular position of the same radius. The distance may be constant.

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

Similarly, in the rear housing chamber A3, a rear compression chamber A5 is defined by a rear rotor 80 (specifically, a rear rotor surface 90), a rear cylinder inner peripheral surface 56, and a 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, it can be said that the vane 100 causes a volume change in both the compression chambers A4 and A5. This point will be described later.

  Incidentally, 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.

  As shown in FIGS. 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 extending in the radial direction R, for example. However, it is not limited to this, and the shape of the introduction port 111 is arbitrary.

The introduction port 111 passes through the front rotor 60 in the axial direction Z. The introduction port 111 is disposed closer to the outer peripheral end than the inner peripheral end of the front rotor 60.
The introduction port 111 communicates with the front compression chamber A4 in 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 in a phase where the volume of the front compression chamber A4 decreases. Has been.

  Specifically, the introduction port 111 is, for example, near the boundary between the second front flat surface 72 and the front curved surface 73, more specifically, near the circumferential end of the front curved surface 73 on the second front flat surface 72 side. Is provided. Further, focusing on the relationship with the rotation direction of the front rotor 60, 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, and specifically, is formed at a position overlapping the locus of the introduction port 111 when the front rotor 60 rotates when viewed from the axial direction Z. The four communication holes 112 extend in the circumferential direction of the rotating shaft 12, and in the present embodiment, four communication holes 112 are formed in a state of being separated from each other in the circumferential direction. Thereby, even if the position of the introduction port 111 fluctuates with the rotation of the front rotor 60, the state where the introduction port 111 and the communication hole 112 communicate with each other 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, for example. In the present embodiment, the discharge port 113 is circular. However, 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 in 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 in a phase where the volume of the rear compression chamber A5 increases. Has been.

  Specifically, the discharge port 113 is provided, for example, near the boundary between the second rear flat surface 92 and the rear curved surface 93, more specifically, at the circumferential end of the rear curved surface 93 on the second rear flat surface 92 side. It has been. Further, focusing attention on the relationship with the rotation direction of the front rotor 60, 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.

  In the present embodiment, the introduction port 111 and the discharge port 113 pass through the centers of the rotors 60 and 80 when viewed from the axial direction Z, and are opposed to the flat surfaces 71 and 72 (opposite directions of the flat surfaces 91 and 92). ) Is not disposed on both sides of the center line extending to), but is disposed on one side. However, the positions of the introduction port 111 and the discharge port 113 are arbitrary.

  Although not shown, the discharge port 113 may be provided with a discharge valve that closes the discharge port 113 and opens the discharge port 113 based on the application of the specified pressure. However, the discharge valve is not essential and may be omitted.

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 channel 114 that connects the discharge chamber A6 and the discharge port 11b.
The discharge chamber A6 is partitioned 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. Corresponding to the rotation of the discharge port 113, 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, it can suppress that the situation where the discharge port 113 and discharge chamber A6 are not connected arises. According to such a 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.

  In the present embodiment, 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. Both boss portions 121 and 123 rotate as the rotating shaft 12 rotates.

  The front boss portion 121 protrudes from the front rotor surface 70 toward the rear rotor 80. Specifically, the front boss portion 121 protrudes toward the rear rotor surface 90 from the second front flat surface 72. The front boss portion 121 has a cylindrical shape (for example, a cylindrical shape) 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 121 is fitted to the wall through hole 54 from the first wall 52 side in a slidable state. The front boss portion 121 has an annular front boss tip surface 121a.

  As shown in FIG. 3, the front rotary valve 122 is provided on the front boss front end surface 121 a and protrudes from the front boss front end surface 121 a toward the rear rotor 80. Two front rotary valves 122 are provided at positions spaced apart 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 rotary 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.

  As shown in FIGS. 2 and 4, the rear boss portion 123 protrudes from the rear rotor surface 90 toward the front rotor 60. Specifically, the rear boss portion 123 protrudes toward the front rotor surface 70 from the second rear flat surface 92. The rear boss portion 123 has a cylindrical shape (for example, a cylindrical shape) 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 the wall portion through hole 54 from the second wall surface 53 side in a slidable state. The rear boss portion 123 has an annular rear boss front end surface 123a.

  The rear rotary valve 124 is provided on the rear boss front end surface 123 a and protrudes from the rear boss front end surface 123 a toward the front rotor 60. The rear rotary valve 124 has a columnar shape having, for example, 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 length in the circumferential direction of the rear rotary valve 124 is the same as the circumferential distance between the two front rotary valves 122.

  As shown in FIGS. 8 and 9, the rear rotary valve 124 is engaged with the two front rotary valves 122 in the circumferential direction. Specifically, the rear rotary valve 124 is sandwiched between the two front rotary valves 122 from the circumferential direction. That is, both rotary valves 122 and 124 are fitted. The two rotors 60 and 80 have their relative positions in the circumferential direction defined by the engagement of the rotary valves 122 and 124.

  Here, one fan-like connection valve 125 is formed by both the front rotary valve 122 and the rear rotary valve 124. The connection valve 125 is disposed in the wall through hole 54. That is, the rotary valves 122 and 124 are engaged in the wall through hole 54.

  The connecting valve 125 is not a closed ring shape but a fan shape. Therefore, an open space 126 in which fluid can move is formed in the wall through hole 54, specifically between the rotary shaft 12 and the wall inner peripheral surface 54 a that is the inner peripheral surface of the wall through hole 54. Has been. The open space 126 is a space defined 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 54 a.

  The connecting valve 125 has a valve outer peripheral surface 125 a having the same diameter as that of 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. In the present embodiment, since the outer peripheral surfaces of the rotary valves 122 and 124 are flush with each other, the valve outer peripheral surface 125a is one continuous peripheral surface. The valve outer peripheral surface 125 a is in contact with the wall inner peripheral surface 54 a that is the inner peripheral surface of the wall through hole 54. The wall inner peripheral surface 54a can also be said to be the inner peripheral surface of the intermediate wall portion 51 formed in a ring shape.

  Incidentally, the height of the front rotary valve 122 and the height of the rear rotary valve 124 are the same. The heights of the rotary valves 122 and 124 are the protruding dimensions of the rotary valves 122 and 124, and specifically the length in the axial direction Z from the boss tip surfaces 121a and 123a. As shown in FIGS. 4 and 5, the front end surface 122a of the front rotary valve 122 is in contact with the rear boss front end surface 123a, and the front end surface 124a of the rear rotary valve 124 is in contact with the front boss front end surface 121a. . By these abutments, the relative positions in the axial direction Z of both rotors 60 and 80 are defined.

  A protrusion 127 is provided separately from the rear rotary valve 124 on the rear boss front end surface 123a. The protrusion 127 is provided at a point-symmetrical position with respect to the rear rotary valve 124 with the rotating shaft 12 as the center. The inner peripheral surface of the protrusion 127 is in contact with the rotating shaft 12, and the rotating shaft 12 is sandwiched between the protrusion 127 and the rear rotary valve 124. Thereby, the positional deviation of the rear rotor 80 in the direction orthogonal to the axial direction Z is restricted.

Incidentally, the outer diameter of the protrusion 127 is set smaller than the diameter of the wall portion through hole 54. For this reason, a gap exists between the protrusion 127 and the wall inner peripheral surface 54a.
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. 8, the front opening 131 and the rear opening 132 are formed in the intermediate wall 51. Both openings 131 and 132 are formed to be spaced apart from each other in the circumferential direction of the rotors 60 and 80. In the present embodiment, the front-side opening 131 and the rear-side opening 132 are disposed on both sides of the vane 100. Specifically, a front-side opening 131 is formed on one end side in the circumferential direction of the vane 100 (in other words, on the side opposite to the rotation direction of the rotors 60 and 80), and the other end side in the circumferential direction of the vane 100. A rear side opening 132 is formed on the other side (in other words, on the rotational direction side of the rotors 60 and 80). Note that the openings 131 and 132 and the vane groove 110 communicate with each other.

  As shown in FIG. 2, the front opening 131 opens toward the front compression chamber A <b> 4 and the wall through hole 54. Specifically, 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, and the fluid in the front compression chamber A4 passes through the front opening 131. It is configured to be able to flow into the part through hole 54.

  On the other hand, as shown in FIG. 3, the front-side opening 131 is not formed on the second wall surface 53. That is, the front side opening 131 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.

  The rear side opening 132 opens toward the rear compression chamber A5 and the wall through hole 54. Specifically, the rear side opening 132 is formed on both the second wall surface 53 and the wall inner peripheral surface 54a of the intermediate wall 51, and the fluid in the rear compression chamber A5 passes through the rear side opening 132. It is configured to be able to flow into the part 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.

  In the present embodiment, as shown in FIG. 8, the front-side opening 131 is half U-shaped and extends in the radial direction R. The rear side opening 132 has a semi-U shape symmetrical to the front side opening 131. However, the specific shapes of the openings 131 and 132 are not limited to this and are arbitrary.

  Here, the front opening 131 and the rear opening 132 are partitioned by the vane 100. The vane 100 restricts the flow of fluid directly from the front opening 131 toward the rear opening 132.

  As shown in FIG. 8, the communication groove 133 is formed to be recessed outward in the radial direction R 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 also communicates with the open space 126. In addition, since the circumferential direction of the wall inner peripheral surface 54a and the circumferential direction of both the rotors 60 and 80 coincide, it can be said that the circumferential direction of the wall inner peripheral surface 54a is the circumferential direction of both the rotors 60 and 80.

  On the other hand, the communication groove 133 is not in direct communication with the front opening 131, and the communication groove 133 and the front opening 131 are separated in the circumferential direction of the wall inner peripheral surface 54a. For this reason, the direct flow of fluid from the front opening 131 toward the communication groove 133 is restricted. And between the communication groove 133 and the front side opening part 131 in the wall part internal peripheral surface 54a, the groove-less surface 54aa in which the communication groove 133 is not formed exists.

  According to this configuration, since the fluid is restricted from flowing directly from the front side opening 131 toward the communication groove 133, the fluid passes through the wall portion through hole 54 on the inner side in the radial direction R from the front side opening 131. Flows into the communication groove 133 through the inside of the wall portion through hole 54 (specifically, the inner side in the radial direction R of the grooveless surface 54aa), and then flows to the rear side opening 132.

  Here, as shown in FIG. 8, when the connection valve 125 is arranged inside the front side opening 131 in the radial direction R, the connection valve 125 blocks the opening portion inside the front side opening 131 in the radial direction R. Can be removed. 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 the present embodiment, the position where the connecting valve 125 closes the front side opening 131 and the position inside the radial direction R in the front side opening 131 correspond to the “closed position”.

  In particular, in the present embodiment, when the connection valve 125 is disposed on the inner side in the radial direction R 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. Yes. As a result, the connecting valve 125 is interposed between the front opening 131 and the communication groove 133. Therefore, the fluid leakage from the front opening 131 toward the communication groove 133 is restricted by the contact between the connection valve 125 and the grooveless surface 54aa.

  On the other hand, as shown in FIG. 9, as the rotors 60 and 80 rotate, the connecting valve 125 is disposed at a position shifted 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 inner side in the radial direction R of the front side opening 131. In addition, since the connection valve 125 is not disposed on the inner side in the radial direction R with respect to the grooveless surface 54aa, the connection valve 125 may cause the fluid that flows into the wall through hole 54 from the front side opening 131 to flow into the communication groove 133. It is difficult for the situation to be obstructed by. 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 can move 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. That is, the compression chambers A4 and A5 are in communication with each other.

  In the present embodiment, the position where the connecting valve 125 is displaced with respect to the opening portion inside the radial direction R of the front side opening 131, in other words, the position where the connecting valve 125 does not block the front side opening 131 is “open. Corresponds to “position”.

  In other words, the connection valve 125 is provided on the communication flow path 130, and according to the angular position of both the rotors 60 and 80, an open position for opening the communication flow path 130 and a closed position for closing the communication flow path 130. It can be said that it is something to move to. In other words, in the communication mechanism 120, the communication flow path 130 is blocked by the connection valve 125 and the communication state in which the communication flow path 130 is connected through the open space 126 according to the rotational positions of the rotors 60 and 80. It can be said that it switches to a non-communication state.

  Incidentally, even if the valve outer peripheral surface 125a and the groove-less surface 54aa are in contact with each other, the diameters of both the openings 131 and 132 so that the open space 126 straddles the radial direction R inner region of the vane 100. When arranged in the direction R inner region, fluid movement between the front side opening 131 and the rear side opening 132 is allowed through the inner region of the vane 100.

  In such a configuration, depending on the circumferential length of the valve outer peripheral surface 125a (in other words, the angular range occupied by the connecting valve 125), the front compression chamber A4 and the rear compression chamber A5 are included in one rotation period of the rotors 60 and 80. The period during which is communicated 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 for communicating both compression chambers A4 and A5 and the period for communicating can be adjusted.

  Incidentally, as shown in FIGS. 8 and 9, the inner end surface 103 which is the end surface on the inner side in the radial direction R of the vane 100 is in contact with the outer peripheral surfaces of both the boss portions 121 and 123 and the valve outer peripheral surface 125 a. In the present embodiment, the outer peripheral surfaces of both boss portions 121 and 123 are flush with each other, and the outer peripheral surface of both boss portions 121 and 123 and the valve outer peripheral surface 125a (the outer peripheral surfaces of both rotary valves 122 and 124). It is the same. 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. The inner end surface 103 of the vane 100, the outer peripheral surfaces of the boss portions 121 and 123, and the valve outer peripheral surface 125a are in surface contact.

  An outer end surface 104 that is an end surface on the outer side in the radial direction R of the vane 100 is flush with the first part surface 57 a 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.

  That is, 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 125 a, 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.

  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 in this embodiment will be described in detail with reference to FIGS.

  FIG. 10B is a development view showing the state of the rotors 60 and 80 and the vane 100 in the state shown in FIG. 10A, and FIG. 11B shows both states in the state shown in FIG. FIG. 3 is a development view showing a state of the rotors 60 and 80 and the vane 100. 10B and 11B, both the openings 131 and 132 are schematically shown in the intermediate wall 51, and the open space 126 is schematically shown. 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.

  As shown in FIGS. 10A and 10B, when the vane 100 is in contact with the second front flat surface 72 and the first rear flat surface 91, the vane 100 enters the front storage chamber A2. Not. In this case, there is one front compression chamber A4, and the front compression chamber A4 is filled with suction fluid. That is, 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, the rear housing chamber A3 includes two rear compression chambers A5 (hereinafter referred to as a first rear compression chamber A5a and a second rear chamber). Rear compression chamber A5b) is formed. The first rear compression chamber A5a and the second rear compression chamber A5b are partitioned by a contact portion between the second rear flat surface 92 and the second wall surface 53 and the vane 100, 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.

  That is, the vane 100 communicates with the first rear compression chamber A5a communicating with the rear side opening 132 and the discharge port 113 so that the rear side opening 132 and the discharge port 113 do not directly communicate with each other. It can also be said that it partitions the 2 rear compression chamber A5b.

  Thereafter, when the rotating shaft 12 is rotated by the electric motor 13, both the rotors 60 and 80 are rotated accordingly. In FIG. 10B, both rotors 60 and 80 move downward in the drawing. As a result, the vane 100 moves in the axial direction Z (the left-right direction in FIG. 10B), and a part of the vane 100 enters the front storage chamber A2. Thus, as shown in FIG. 11B, two front compression chambers A4 (hereinafter referred to as a first front compression chamber A4a and a second front compression chamber A4b) having the vane 100 as a boundary are formed. The first front compression chamber A4a and the second front compression chamber A4b are partitioned by the vane 100 and the contact portion between the second front flat surface 72 and the first wall surface 52, 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 side opening 131. On the other hand, the second front compression chamber A4b communicates with the front opening 131, but does not communicate with the introduction port 111.

  That is, the vane 100 communicates with the first front compression chamber A4a communicating with the introduction port 111 and the front opening 131 so that the introduction port 111 and the front opening 131 do not directly communicate with each other. It can also be said that the two front compression chambers A4b are partitioned.

  And when both rotors 60 and 80 rotate in the state divided by the vane 100, a volume change arises in both compression chambers A4 and A5. Specifically, in the first front compression chamber A4a, the volume increases and suction fluid is sucked from the introduction port 111, while in the second front compression chamber A4b, the volume decreases and suction fluid is compressed. Similarly, in the second rear compression chamber A5b, the volume is reduced and the fluid is compressed. In addition, although space itself becomes large in 1st rear compression chamber A5a, since the communication mechanism 120 is a non-communication state, a fluid does not flow into 1st rear compression chamber A5a.

  Thereafter, as shown in FIGS. 11A and 11B, after the vane 100 passes through the first front flat surface 71 and the second rear flat surface 92, both compression chambers A4 and A5 (in detail, The two front compression chambers A4b and the first rear compression chamber A5a) communicate with each other. 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 communicates 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 discharged from the discharge port 113 has a higher pressure than the intermediate pressure fluid.

  As described above, when the rotors 60 and 80 rotate, both the compression chambers A4 and A5 repeatedly perform the suction and compression cycle operations with one cycle of 720 ° (two rotations of the rotors 60 and 80). Yes. In particular, in the present embodiment, 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.

  Here, for convenience of explanation, the two front compression chambers A4a and A4b have been described separately. However, if attention is paid to the fact that the front compression chamber A4 performs a cycle operation with one cycle of 720 °, the first front compression chamber A4a. Can be said to be a front compression chamber A4 having a phase of 0 ° to 360 °, and the second front compression chamber A4b can be said to be a front compression chamber A4 having a phase of 360 ° to 720 °. That is, the space defined by the front rotor surface 70, the first wall surface 52, and the front cylinder inner peripheral surface 43 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. It can also be said that it is partitioned from the front compression chamber A4. In other words, the vane 100 divides the space into the first chamber into which the fluid is sucked and the second chamber into which the fluid is discharged, and the first chamber according to the rotation of the rotors 60 and 80. In addition, it can be said that the volume change of the second chamber (specifically, volume increase for the first chamber and volume decrease for the second chamber) is caused. The same applies to the first rear compression chamber A5a and the second rear compression chamber A5b.

  The communication channel 130 includes a front compression chamber A4 having a phase of 360 ° to 720 ° (in other words, a compression stage) and a rear compression chamber A5 having a phase of 0 ° to 360 ° (in other words, the suction stage). It can be said that this is a flow path for communication. And it can be said that the communication mechanism 120 makes the front compression chamber A4 whose phase is 360 ° to 720 ° and the rear compression chamber A5 whose phase is 0 ° to 360 ° communicate with each other.

  Next, the volume change of both compression chambers A4 and A5 will be described as an operation of the present embodiment with reference to FIG. In FIG. 12, 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. 10 total volume changes are shown.

  In this embodiment, a phase difference occurs in 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 facing distance is constant, and the volume of both compression chambers A4 and A5 is changed by one vane 100. This is realized by communicating both compression chambers A4 and A5 in the latter half of the A4 compression stage.

  In the present embodiment, as shown in FIG. 12, 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. Specifically, in the compressor 10 of the present embodiment, 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 intermediate pressure fluid is sucked into the rear compression chamber A5. Is started and the volume of the rear compression chamber A5 is increased. For this reason, as shown by the solid line in FIG. 12, 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.

According to the embodiment described above in detail, the following effects are obtained.
(1-1) The compressor 10 includes rotors 60 and 80 that are arranged to face each other in the axial direction Z and rotate in accordance with the rotation of the rotary shaft 12, and the cylinder inner circumference that opposes the rotor outer circumferential surfaces 62 and 82 in the radial direction R. Cylinder side walls 42 and 55 having surfaces 43 and 56 and accommodating rotors 60 and 80 are provided. The rotors 60 and 80 have ring-shaped rotor surfaces 70 and 90. The compressor 10 is disposed between the rotors 60 and 80, and has an intermediate wall portion 51 having wall surfaces 52 and 53 opposed to the rotor surfaces 70 and 90 in the axial direction Z, and a vane groove formed in the intermediate wall portion 51. And a vane 100 that abuts against both rotor surfaces 70 and 90 in a state of being inserted into the rotor 110. The vane 100 moves in the axial direction Z as the rotors 60 and 80 rotate.

  In such a configuration, the compressor 10 includes compression chambers A4 and A5 in which the volume is changed by the vane 100 as the rotors 60 and 80 rotate, and fluid is sucked and compressed. The front compression chamber A4 is partitioned by a front rotor surface 70, a first wall surface 52, and a front cylinder inner peripheral surface 43. The rear compression chamber A5 is partitioned by a rear rotor surface 90, a second wall surface 53, and a rear cylinder inner peripheral surface 56. The compressor 10 includes a communication mechanism 120 that switches between a communication state in which the compression chambers A4 and A5 are in communication and a non-communication state in which the compression chambers A4 and A5 are not in communication.

  According to such a configuration, when the rotors 60 and 80 are rotated, fluid is sucked and compressed in the compression chambers A4 and A5 while the vane 100 moves in the axial direction Z. Further, according to this configuration, the communication mechanism 120 can cause the compression chambers A4 and A5 to communicate with each other or not to communicate with each other. Thereby, for example, the fluid compressed in the front compression chamber A4 can flow into the rear compression chamber A5 and be compressed again.

  (1-2) Since the vane 100 is inserted into the vane groove 110, movement of the rotors 60 and 80 in the circumferential direction is restricted. Thus, the rotation of the vane 100 with the rotation of the rotors 60 and 80 is restricted. Therefore, inconvenience due to the rotation of the vane 100, specifically, the application of centrifugal force to the vane 100 can be suppressed. Therefore, application of excessive force to the vane 100 can be suppressed.

  (1-3) The wall portion through hole 54 having a diameter larger than that of the rotating shaft 12 is formed in the intermediate wall portion 51. The communication mechanism 120 includes a communication flow path 130 that allows the compression chambers A4 and A5 to communicate with each other via the rotation shaft 12 and a wall inner peripheral surface 54a that is an inner peripheral surface of the wall through hole 54, and both rotors 60. , 80 according to the angular position, and a connection valve 125 that moves to an open position that opens the communication flow path 130 and a closed position that closes (in other words, shuts off) the communication flow path 130.

  According to such a configuration, the connection valve 125 moves between the open position and the closed position as the rotors 60 and 80 rotate, so that the communication state or the non-communication state can be set according to the angular position. .

  In particular, according to the present embodiment, the communication flow path 130 communicates between the rotary shaft 12 and the wall inner peripheral surface 54a, and thus, for example, the two rotors 60, so as to bypass the intermediate wall 51. Compared with the configuration in which the communication flow path is provided outside the 80 radial direction R, the compressor 10 can be prevented from being enlarged in the radial direction R.

  (1-4) The communication flow path 130 includes a communication groove 133 that is recessed outward in the radial direction R from the wall inner peripheral surface 54a, a front-side opening 131, and a rear-side opening 132. The front opening 131 is formed in the intermediate wall 51 and opens toward the front compression chamber A4 and the wall through hole 54. The rear side opening 132 is formed at a position different from the front side opening 131 in the intermediate wall portion 51 in the circumferential direction, and opens toward the rear compression chamber A5 and the wall portion through hole 54.

  The connecting valve 125 is disposed in the wall through hole 54 and has a fan shape. Therefore, an open space 126 that communicates with the communication groove 133 is formed in the wall portion through hole 54. Further, a valve outer peripheral surface 125a, which is an outer peripheral surface of the connection valve 125, is in contact with the wall inner peripheral surface 54a. The communication groove 133 communicates with either one of the openings 131 and 132 (in this embodiment, the rear side opening 132), while the other opening (in this embodiment, the front side opening 131). ).

  In such a configuration, when the connection valve 125 is disposed at the closed position, the connection valve 125 is disposed inside the radial direction R of the portion of the front side opening 131 that opens toward the wall through hole 54, and the opening thereof. The portion is closed by the valve outer peripheral surface 125a. On the other hand, when the connection valve 125 is disposed at the open position, the connection valve 125 is disposed at a position shifted in the circumferential direction of the rotors 60 and 80 with respect to the opening portion of the front side opening 131, and the open space 126. The fluid is allowed to move between the compression chambers A4 and A5.

  According to such a configuration, the two rotors 60 and 80 are automatically switched between a communication state and a non-communication state. As a result, both the compression chambers A4 and A5 can be communicated or not communicated during one rotation of the rotors 60 and 80.

  In particular, according to this configuration, the period in which the compression chambers A4 and A5 are communicated can be adjusted by adjusting the circumferential length of the valve outer peripheral surface 125a. Further, by adjusting the angular position of the connecting valve 125, the timing at which the compression chambers A4 and A5 communicate with each other can be adjusted. As a result, it is possible to easily and freely adjust the communication / non-communication between the compression chambers A4 and A5.

  (1-5) The communication mechanism 120 includes cylindrical boss portions 121 and 123 protruding in a direction approaching each other from inner peripheral end portions of the rotors 60 and 80, and a boss tip surface 121a that is a tip surface of the boss portions 121 and 123. , 123a and rotary valves 122, 124 as engaging portions protruding in a direction approaching each other. The rotary valves 122 and 124 are engaged with each other in the circumferential direction of the rotors 60 and 80 (in other words, the rotational direction of the rotors 60 and 80). The connecting valve 125 is constituted by both rotary valves 122 and 124, and the valve outer circumferential surface 125 a is constituted by the outer circumferential surfaces of both rotary valves 122 and 124.

  According to this configuration, the rotors 60 and 80 are engaged by the rotary valves 122 and 124 that constitute the connection valve 125 that switches between the communication state and the non-communication state. Thereby, since the relative position of both the rotors 60 and 80 in the circumferential direction of both the rotors 60 and 80 is prescribed | regulated, the position shift of both the rotors 60 and 80 in the circumferential direction of both the rotors 60 and 80 can be suppressed.

  In particular, since the rotary valves 122 and 124 are engaged in the circumferential direction, the relative position varies due to the engagement of the rotary valves 122 and 124 even when the rotors 60 and 80 are rotating. Hard to do. Thereby, the fluctuation | variation of the said relative position during rotation of both the rotors 60 and 80 can be suppressed. In addition, the rotational force of one of the rotors 60 and 80 is transmitted to the other through the engaging part of the rotary valves 122 and 124. Thereby, rotation of both rotors 60 and 80 can be synchronized more.

  (1-6) The vane 100 includes a first vane end 101 and a second vane end 102 which are both ends in the axial direction Z. The vane end portions 101 and 102 are in contact with the rotor surfaces 70 and 90. The front rotor surface 70 has a front curved surface 73 that is displaced in the axial direction Z according to its angular position. The rear rotor surface 90 has a rear curved surface 93 that is displaced in the axial direction Z according to the angular position. The front curved surface 73 and the rear curved surface 93 are opposed to each other in the axial direction Z via the intermediate wall portion 51, and are curved in the axial direction Z so that the facing distance is constant regardless of the angular position. .

  According to such a configuration, when the rotors 60 and 80 are rotated, the vane 100 is moved along the rotor surfaces 70 and 90, so that the vane 100 is naturally moved in the axial direction Z. Thereby, it is not necessary to separately provide a configuration for moving the vane 100, and the configuration can be simplified.

  Note that the facing distance between the curved surfaces 73 and 93 is constant regardless of the angular position if the rotors 60 and 80 can rotate with the vane end portions 101 and 102 in contact with the curved surfaces 73 and 93. Includes some errors.

  (1-7) The vane end portions 101 and 102 do not intermittently contact the rotor surfaces 70 and 90 but continuously contact the rotor surfaces 70 and 90. That is, the vane end portions 101 and 102 slide with respect to the rotor surfaces 70 and 90. According to such a configuration, it is difficult to generate a sound when the vane end portions 101 and 102 hit the rotor surfaces 70 and 90, so that the quietness can be improved.

  (1-8) The front rotor surface 70 includes both front flat surfaces 71 and 72 arranged at positions shifted in the axial direction Z from each other. The second front flat surface 72 is in contact with the first wall surface 52. The front curved surface 73 connects both front flat surfaces 71 and 72. The rear rotor surface 90 includes both rear flat surfaces 91 and 92 arranged at positions shifted from each other in the axial direction Z. 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 such a configuration, the contact between the second front flat surface 72 and the first wall surface 52 causes the front compression chamber A4 (first front compression chamber A4a) on the suction side to be in contact with the front on the compression side. The communication with the compression chamber A4 (second front compression chamber A4b) is restricted. Thereby, the leakage of the fluid can be suppressed and the efficiency can be improved. Further, since the first rear flat surface 91 is disposed at a position facing the second front flat surface 72 so as to correspond to the second front flat surface 72, the facing distance between them can be made constant, and the vane It is possible to prevent the movement of 100 from being hindered, and to suppress the generation of a gap between the vane 100 and both rotor surfaces 70 and 90. The same applies to the rear compression chamber A5.

  (1-9) The compressor 10 includes a housing 11 in which the rotary shaft 12 is accommodated, and two radial bearings 32 and 34 that are supported on the housing 11 in a state where both ends of the rotary shaft 12 are rotatable. Yes.

  According to this configuration, since both end portions of the rotating shaft 12 are rotatably supported by the radial bearings 32 and 34, only one end portion of the rotating shaft 12 is supported by the radial bearing like a scroll compressor. Compared with the structure which exists, the rotating shaft 12 can be supported stably. Thereby, it can respond to high-speed rotation.

  (1-10) The compressor 10 includes a first front compression chamber A4a and a second front compression chamber A4b partitioned by the vane 100 as the front compression chamber A4, and a first partition partitioned by the vane 100 as the rear compression chamber A5. 1 rear compression chamber A5a and 2nd rear compression chamber A5b.

  The first front compression chamber A4a has a volume that increases with the rotation of the front rotor 60, and is configured such that a suction fluid is sucked therein. The second front compression chamber A4b is configured such that the volume decreases as the front rotor 60 rotates.

  The first rear compression chamber A5a is configured to increase in volume with the rotation of the rear rotor 80. The second rear compression chamber A5b has a volume that decreases with the rotation of the rear rotor 80, and is configured to discharge fluid.

  In such a configuration, the communication mechanism 120 switches between a communication state in which the second front compression chamber A4b and the first rear compression chamber A5a are in communication and a non-communication state in which the compression chambers A4b and A5a are not in communication. . Accordingly, the intermediate pressure fluid compressed in the second front compression chamber A4b can be supplied to the first rear compression chamber A5a in the suction stage, and can be further compressed in the second rear compression chamber A5b.

(Second Embodiment)
In the present embodiment, the suction and compression cycle operations are different from those in the first embodiment. The different points will be described in detail below.

  As shown in FIG. 13, the compressor 10 of the present embodiment is configured such that the suction fluid is sucked not only into the front compression chamber A4 but also into the rear compression chamber A5. Specifically, the compressor 10 includes a rear suction channel 141 that introduces suction fluid into the rear compression chamber A5, and an opening / closing part 142 that opens and closes the rear suction channel 141.

  In the present embodiment, the rear-side suction channel 141 allows the motor chamber A1 and the rear compression chamber A5 to communicate with each other. The rear side suction flow path 141 is formed in the housing 11 and penetrates the front cylinder 40 and the rear cylinder 50. The rear-side suction channel 141 communicates with the first rear compression chamber A5a that communicates with the rear-side opening 132 in the rear compression chamber A5.

  The opening / closing part 142 is provided on the rear side suction flow path 141 and switches between a closed state in which the rear side suction flow path 141 is closed and an open state in which the rear side suction flow path 141 is opened. The closed state is a state in which the suction fluid in the motor chamber A1 is restricted from flowing into the rear compression chamber A5 via the rear-side suction flow path 141. The open state is a state in which the suction fluid in the motor chamber A1 is allowed to flow into the rear compression chamber A5 via the rear side suction flow path 141. With the opening / closing part 142, the suction of the suction fluid into the rear compression chamber A5 can be started or stopped.

In addition, the specific structure of the opening / closing part 142 is arbitrary, for example, a structure using a rotary valve as in the first embodiment, a structure using an electromagnetic valve, or the like.
Next, the communication mechanism 150 of this embodiment will be described.

As shown in FIG. 14, the communication mechanism 150 of this embodiment includes a front rotary valve 151 and a rear rotary valve 152.
Two front rotary valves 151 are provided at positions spaced apart in the circumferential direction, and both front rotary valves 151 are arranged to face each other.

  Two rear rotary valves 152 are provided at positions spaced apart in the circumferential direction. Both the rear rotary valves 152 are columnar shapes having curved inner peripheral surfaces and outer peripheral surfaces, for example. Both the rear rotary valves 152 are disposed to face each other in a direction orthogonal to the facing direction of both the front rotary valves 151. Both the rear rotary valves 152 are arranged between the front rotary valves 151.

  The rear rotary valve 152 is engaged with the two front rotary valves 151 in the circumferential direction. Specifically, the rotary valves 151 and 152 are sandwiched from each other in the circumferential direction. That is, both rotary valves 151 and 152 are engaged with each other. The two rotors 60 and 80 have their relative positions in the circumferential direction defined by the mutual engagement of the rotary valves 151 and 152.

  Here, the front rotary valve 151 and the rear rotary valve 152 form one closed ring-shaped connection valve 153. The connection valve 153 is disposed in the wall through hole 54. That is, the rotary valves 151 and 152 are engaged in the wall through hole 54. The connecting valve 153 has a valve outer peripheral surface 153a that comes into contact with the wall inner peripheral surface 54a.

  The communication mechanism 150 includes a communication channel 160 that allows the compression chambers A4 and A5 to communicate with each other. The communication channel 160 includes a front side opening 161, a rear side opening 162, and a communication groove 163.

The front opening 161 and the rear opening 162 are formed in the intermediate wall 51. Both openings 161 and 162 are formed to be spaced apart from each other in the circumferential direction of the rotors 60 and 80.
In the present embodiment, the front-side opening 161 is disposed next to the vane 100. More specifically, a front-side opening 161 is formed on one end side in the circumferential direction of the vane 100 (in other words, on the side opposite to the rotational direction of the rotors 60 and 80). The front opening 161 and the vane groove 110 communicate with each other.

  In the present embodiment, the rear side opening 162 is disposed at a position shifted by 180 ° with respect to the front side opening 161, for example. Both openings 161 and 162 are arranged at point-symmetrical positions with respect to the central axis of the rotating shaft 12.

  Similar to the first embodiment, the front opening 161 is formed on the first wall surface 52 of the intermediate wall 51, but is not formed on the second wall 53. The rear side opening 162 is formed on the second wall surface 53 in the intermediate wall portion 51, but is not formed on the first wall surface 52. That is, both the openings 161 and 162 do not penetrate the intermediate wall portion 51 in the axial direction Z, and do not directly connect the front compression chamber A4 and the rear compression chamber A5.

  The communication groove 163 of the present embodiment extends in the circumferential direction of the wall portion inner peripheral surface 54 a and communicates with both the openings 161 and 162. Specifically, the communication groove 163 is formed over the half circumference of the wall inner peripheral surface 54 a so as to connect both the openings 161 and 162 while bypassing the vane 100.

According to such a configuration, the fluid in the front compression chamber A4 can flow into the rear compression chamber A5 via the front side opening 161 → the communication groove 163 → the rear side opening 162.
Next, the relationship between the positions of the two openings 161 and 162 and the compression chambers A4 and A5 in the present embodiment will be described in detail with reference to FIGS.

  As already described, the rear side opening 162 is disposed at a position different from the front side opening 161 by 180 °. And in the state shown in FIG. 15, since the rear side opening 162 is closed by the second rear flat surface 92, the compression chambers A4 and A5 are not in communication. Thereafter, when the rotors 60 and 80 are rotated, the second front compression chamber A4b and the first rear compression chamber A5a communicate with each other through the communication flow path 160. After that, as shown in FIG. 16, when the second rear flat surface 92 passes through the vane 100, the second front compression chamber A4b and the second rear compression chamber A5b communicate with each other through the communication channel 160. Then, the rear side opening 162 is closed again by the second rear flat surface 92, whereby the compression chambers A4 and A5 are disconnected.

  That is, it can be said that the communication mechanism 150 (communication flow path 160) is a flow path that connects the front compression chamber A4 having a phase of 360 ° to 720 ° and the rear compression chamber A5 having a phase of 180 ° to 540 °. In other words, it can be said that the communication mechanism 150 of the present embodiment communicates the front compression chamber A4 at the stage where the volume decreases with the rear compression chamber A5 at the stage where the volume switches from increase to decrease.

  Thereafter, when the rotors 60 and 80 rotate to a position where the vane 100 contacts the second front flat surface 72 and the first rear flat surface 91, all the compressed fluid in the second front compression chamber A4b passes through the rear compression chamber A5. And discharged from the discharge port 113.

In addition, the suction fluid sucked into the first front compression chamber A4a is pressure-fed or compressed as the fluid in the second front compression chamber A4b when the next rotors 60 and 80 are rotated.
As described above, in both the compression chambers A4 and A5, by performing a cycle operation in which one cycle of the two revolutions (720 °) of the rotors 60 and 80 is performed, fluid suction and fluid pumping or compression are performed. Is called.

  Here, the rear suction channel 141 communicates with the first rear compression chamber A5a. And the opening-and-closing part 142 will be in an open state over the period from 0 degree to the specific phase of the rear compression chamber A5. As a result, the suction fluid is sucked into the rear compression chamber A5. The specific phase is, for example, 360 ° or less. The specific phase will be described later.

A series of suction / compression cycle operations performed in both compression chambers A4 and A5 in this embodiment will be described with reference to FIG.
As shown in FIG. 17A, the compressor 10 of the present embodiment is configured such that a phase difference is generated between the volume change of the front compression chamber A4 and the volume change of the rear storage chamber A3. The volume change of the rear compression chamber A5 is configured so as to be delayed in phase with respect to the volume change of the front compression chamber A4.

  The phase difference is such that both rotor surfaces 70 and 90 are curved in the axial direction Z so that the facing distance is constant, and the volume change of both compression chambers A4 and A5 is realized by one vane 100. This is realized by the fact that the suction fluid is sucked over the phase of the compression chamber A5 from 0 ° to a specific phase.

  Specifically, as shown in FIGS. 17 (a) and 17 (b), the compressor 10 of the present embodiment sucks suction fluid into the front compression chamber A4 (hereinafter referred to as “front compression chamber A4”). After the start of “suction operation”, the opening / closing part 142 is opened, and suction of suction fluid into the rear compression chamber A5 (hereinafter also referred to as “suction operation of the rear compression chamber A5”) is started. It is comprised so that. As a result, the suction fluid is sucked in both the compression chambers A4 and A5. Thereafter, when the suction of the front compression chamber A4 started earlier is finished, the volume reduction of the front compression chamber A4 is started.

  Here, as shown in FIGS. 17A and 17C, the communication mechanism 120 of the present embodiment is configured to be opened at a timing (360 °) when the suction of the front compression chamber A4 is completed. Has been. Thereby, both compression chambers A4 and A5 communicate. For this reason, as the volume of the front compression chamber A4 decreases, the suction fluid in the front compression chamber A4 is pumped to the rear compression chamber A5 via the communication mechanism 120 (hereinafter, also referred to as “pressure feeding operation of the front compression chamber A4”). ). At this stage, the suction operation of the rear compression chamber A5 is continued.

  That is, the pressure compression operation of the front compression chamber A4 and the suction operation of the rear compression chamber A5 are performed in a state where both the compression chambers A4 and A5 are in communication. In such a state, the suction fluid is sucked into the rear compression chamber A5 from both the front compression chamber A4 and the rear-side suction flow path 141. Thereby, even after the suction operation of the front compression chamber A4 is completed, the substantial volume of both the compression chambers A4 and A5, that is, the volume of the entire compressor 10 continues to increase.

  Thereafter, as shown in FIGS. 17A and 17B, the opening / closing part 142 is closed at a specific phase corresponding to the timing at which the entire volume of the compressor 10 is maximized. Thus, the suction operation of the rear compression chamber A5 is completed, and the compression of the fluid stored in the rear compression chamber A5 in the rear compression chamber A5 (hereinafter also referred to as “rear compression chamber A5 compression operation”) is started. Is done. Similarly, fluid compression (hereinafter, also referred to as “compression operation of the front compression chamber A4”) is performed in the front compression chamber A4. In this case, both compression chambers A4 and A5 are in communication.

  That is, the compressor 10 of the present embodiment is configured such that the compression operation is performed in both the compression chambers A4 and A5 in a state where the both compression chambers A4 and A5 are in communication. In the following description, the compression operation of both compression chambers A4 and A5 in a state where both compression chambers A4 and A5 are in communication is referred to as a parallel compression operation.

  Thereafter, the compression operation of the front compression chamber A4 ends during the compression operation of the rear compression chamber A5. Then, as shown in FIGS. 17A and 17C, the communication mechanism 120 enters a non-communication state in synchronization with the end of the compression operation of the front compression chamber A4.

  After the compression operation of the front compression chamber A4 is completed, only the compression operation of the rear compression chamber A5 is continuously performed. When the compression operation is completed, one cycle of suction / compression in the compressor 10 is completed. To do.

That is, the cycle operation performed by the compressor 10 of this embodiment is
(A) Front suction operation in which the suction operation of the front compression chamber A4 is performed while the suction operation of the rear compression chamber A5 is not performed in a state where the compression chambers A4 and A5 are not in communication.
(B) Parallel suction operation in which suction fluid is sucked into the compression chambers A4 and A5.
(C) A communication intermediate operation in which the pressure feeding operation of the front compression chamber A4 and the suction operation of the rear compression chamber A5 are performed in a state where both the compression chambers A4 and A5 are in communication.
(D) parallel compression operation,
(E) In a state where the compression chambers A4 and A5 are not in communication, the compression operation of the rear compression chamber A5 is performed, while the rear compression operation in which the compression operation of the front compression chamber A4 is not performed. is there.

Next, the operation of this embodiment will be described.
As shown by the solid line in FIG. 17A, since the suction fluid is sucked into the compression chambers A4 and A5 having different volume change phases, the substantial volume (in other words, the combined compression chambers A4 and A5). For example, the discharge capacity of the main compressor 10 is larger than when the front compression chamber A4 sucks alone. Specifically, even after the volume of the front compression chamber A4 is maximized, the volume of the rear compression chamber A5 increases, so that the overall volume of the compressor 10 increases.

  Thereafter, a communication intermediate operation → parallel compression operation → rear compression operation is performed. Thereby, the substantial volume of both compression chambers A4 and A5 decreases smoothly. Therefore, the substantial volume change in one cycle is not a waveform in which two peaks are generated as in the two-stage compression method shown in FIG. 12, but a smooth waveform having only one peak. That is, a situation in which the volume is locally reduced during one cycle is less likely to occur. Further, as shown by the two-dot chain line in FIG. 17A, in the present embodiment, the pressure of the suction fluid sucked into both the compression chambers A4 and A5 is increased smoothly.

According to the embodiment described above in detail, the following effects are obtained.
(2-1) The compressor 10 is configured such that the suction fluid is sucked into both the compression chambers A4 and A5 whose phase of volume change is shifted. The compressor 10 performs a cycle operation including a parallel suction operation and a parallel compression operation. Specifically, the compressor 10 of the present embodiment is configured to be performed in the order of front suction operation → parallel suction operation → communication intermediate operation → parallel compression operation → rear compression operation. The parallel compression operation is a compression operation in both the compression chambers A4 and A5 in a state where both the compression chambers A4 and A5 are communicated by the communication mechanism 150.

  According to such a configuration, as shown by the solid line in FIG. 17A, the volume change of the entire compressor 10 in one cycle operation can be smoothed. Thereby, the situation where a volume becomes locally small can be suppressed, and generation | occurrence | production of overcompression can be suppressed through it.

Each of the above embodiments may be modified as follows. The above embodiments and 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.
O 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 permitted, 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 shape of both cylinders 40 and 50 is 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 such a 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 that the other rotates. You may attach to the rotating shaft 12 in the state which can be rotated with respect to the shaft 12. FIG. 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.

  O The outer peripheral surfaces of both boss portions 121 and 123 may not be flush with each other but 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. 18 and 19, 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 flow path 201 defines a front-side opening formed in a part 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 formed 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 °. It can be said.

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 such a 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.

  In the second embodiment, in place of the communication intermediate operation, the compression operation of the front compression chamber A4 and the suction operation of the rear compression chamber A5 are performed in a situation where the compression chambers A4 and A5 are not in communication. A configuration in which an intermediate operation is performed may be used.

  ○ 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 two rotary valves 124 are interposed between the two rotary valves 124. The front rotary valve 122 may be disposed and engaged.

The specific position of the openings 131 and 132 is arbitrary as long as the openings 131 and 132 are spaced apart from each other in the circumferential direction.
The communication groove 133 may communicate with the front side opening 131 and be separated from the rear side opening 132. In this case, the opening portion of the rear side opening 132 to the wall through hole 54 is opened or closed by the valve outer peripheral surface 125a, thereby switching between the communication state and the non-communication state.

In the second embodiment, the compression chambers A4 and A5 may communicate with each other during the parallel suction operation.
○ The opening / closing part 142 may be omitted.
In the second embodiment, the suction operation of the front compression chamber A4 may be started after the suction operation of the rear compression chamber A5 is started. In this case, the compression operation of the front compression chamber A4 may be completed after the compression operation of the rear compression chamber A5 is completed.

In the second embodiment, the parallel suction operation may be omitted. In this case, the period during which the suction operations of both the compression chambers A4 and A5 are performed may be adjusted so that the parallel compression operation is performed.
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, but is arbitrary.
(Circle) the fluid of the compression object of the compressor 10 is not restricted to the refrigerant | coolant containing oil, but is arbitrary.
Next, a preferable example that can be grasped from the embodiment and another example will be described below.

  (A) The first rotor surface is provided at a position spaced apart in the axial direction with respect to the first wall surface, and at a position spaced apart in the circumferential direction with respect to the first flat surface orthogonal to the axial direction. And a second flat surface that is perpendicular to the axial direction and is in contact with the first wall surface, and the first curved surface connects the first flat surface and the second flat surface. Yes, it is preferable to bend in the axial direction so as to gradually approach the first wall surface from the first flat surface toward the second flat surface.

  DESCRIPTION OF SYMBOLS 10 ... Compressor, 11 ... Housing, 12 ... Rotary shaft, 32, 34 ... Radial bearing, 40 ... Front cylinder, 42 ... Front cylinder side wall part (1st cylinder part), 43 ... Front cylinder inner peripheral surface (1st inside) Peripheral surface), 50 ... rear cylinder, 51 ... intermediate wall portion (wall portion), 52 ... first wall surface, 53 ... second wall surface, 54 ... wall portion through-hole, 54a ... inner peripheral surface of wall portion, 55 ... side wall of rear cylinder Part (second cylinder part), 56 ... rear cylinder inner peripheral surface (second inner peripheral surface), 60 ... front rotor (first rotor), 62 ... front rotor outer peripheral surface, 70 ... front rotor surface (first rotor surface) , 71, 72 ... Front flat surface, 73 ... Front curved surface (first curved surface), 80 ... Rear rotor (second rotor), 82 ... Rear rotor outer peripheral surface, 90 ... Rear rotor surface (second rotor surface), 91, 92 ... rear flat surface, 93 ... re Curved surface (second curved surface), 100 ... vane, 101 ... first vane end, 102 ... second vane end, 110 ... vane groove, 120, 150, 200 ... communication mechanism, 121 ... front boss (first) 1 boss portion), 121a ... front boss tip surface, 122 ... front rotary valve (first engagement portion), 123 ... rear boss portion (second boss portion), 123a ... rear boss tip surface, 124 ... rear rotary valve (second Engagement portion), 125, 153 ... connection valve (valve), 125a, 153a ... valve outer peripheral surface, 126 ... open space, 130, 160, 201 ... communication channel, 131, 161 ... front side opening (first opening) Part), 132, 162 ... rear side opening part (second opening part), 133, 163 ... communication groove, A4 ... front compression chamber (first compression chamber), A5 ... rear compression chamber (second compression chamber).

Claims (5)

A rotation axis;
A first rotor having a ring-shaped first rotor surface and rotating in accordance with the rotation of the rotating shaft;
A second rotor disposed opposite to the first rotor in the axial direction of the rotating shaft and rotating with the rotation of the rotating shaft, and having a ring-shaped second rotor surface;
A first cylindrical portion having a first inner circumferential surface facing the outer circumferential surface of the first rotor and the radial direction of the rotating shaft, and housing the first rotor;
A second cylindrical portion having a second inner circumferential surface opposed to the outer circumferential surface of the second rotor in the radial direction, and housing the second rotor;
A wall portion disposed between the rotors and having a first wall surface facing the first rotor surface in the axial direction and a second wall surface facing the second rotor surface in the axial direction;
A vane that is in contact with both rotor surfaces in a state of being inserted into a vane groove formed in the wall, and that moves in the axial direction as the rotors rotate;
A first compression chamber that is partitioned by the first rotor surface, the first wall surface, and the first inner peripheral surface, and that changes in volume by the vane as the first rotor rotates and sucks and compresses fluid. When,
A second compression chamber that is partitioned by the second rotor surface, the second wall surface, and the second inner peripheral surface, and in which the volume is changed by the vane as the second rotor rotates to suck and compress the fluid. When,
A communication mechanism that switches between a communication state in which the first compression chamber and the second compression chamber communicate with each other and a non-communication state in which the first compression chamber and the second compression chamber do not communicate with each other;
The compressor characterized by having. In the wall portion, a wall portion through-hole penetrating in the axial direction is formed,
The wall through hole is formed larger in the radial direction than the rotation shaft,
The communication mechanism is
A communication flow path for communicating the first compression chamber and the second compression chamber via the rotation shaft and the inner peripheral surface of the wall through hole;
Depending on the angular position of the two rotors, a valve that moves to an open position that opens the communication flow path and a closed position that closes the communication flow path,
The compressor according to claim 1, comprising: The communication channel is
A communication groove recessed from the inner peripheral surface of the wall through hole to the radially outer side of the rotating shaft;
A first opening formed in the wall and opening toward the first compression chamber and the wall through hole;
A second opening formed at a position different from the first opening in the wall in the circumferential direction and opened toward the second compression chamber and the wall through hole;
Have
The valve is fan-shaped and disposed in the wall through hole, and the valve has a valve outer peripheral surface that comes into contact with an inner peripheral surface of the wall through hole,
The communication groove is in communication with either one of the openings, and is separated from the other opening,
When the valve is disposed in the closed position, the valve is disposed on the radially inner side with respect to an opening portion opened toward the wall through hole in the other opening, and the opening portion is Blocked by the outer peripheral surface of the valve,
When the valve is disposed at the open position, the valve is disposed at a position shifted in the circumferential direction with respect to the opening portion, and is formed in the wall through hole and communicates with the communication groove. The compressor according to claim 2, wherein the fluid is allowed to move from the first compression chamber to the second compression chamber via the. The communication mechanism is
A cylindrical first boss projecting from the inner peripheral end of the first rotor surface toward the second rotor;
A cylindrical second boss projecting from the inner peripheral end of the second rotor surface toward the first rotor;
With
The valve is
A first engagement portion projecting from the tip surface of the first boss portion toward the second rotor;
A second engaging portion that protrudes from the front end surface of the second boss portion toward the first rotor and engages with the first engaging portion in a circumferential direction;
Consists of
The compressor according to claim 3, wherein the outer peripheral surface of the valve is configured by outer peripheral surfaces of the engaging portions. The vane has a first vane end and a second vane end that are both ends in the axial direction,
The first rotor surface with which the first vane end is brought into contact has a first curved surface that is displaced in the axial direction according to the angular position thereof,
The second rotor surface with which the second vane end is in contact has a second curved surface that is displaced in the axial direction according to the angular position thereof,
The first curved surface and the second curved surface are opposed to each other in the axial direction, and are curved in the axial direction so that a facing distance is constant regardless of the angular position. The compressor as described in any one of these.