JP2012117476A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure a passage area for fluid to a working chamber without providing a port groove at an inner circumferential surface.SOLUTION: A compressor comprises inner circumferential surface forming members 10 and 50 to form inner circumferential surfaces 102b, 103b, 503a in a prescribed shape, rotary members 41 42, 81 to rotate in contacting with the inner circumferential surfaces 102b, 103b, 503a, and partitioning members 43, 44, 83 to partition the working chambers 31, 32, 71 formed between the inner circumferential surfaces 102b, 103b, 503a and the rotary members 41, 42, 81. The inner circumferential surface forming members 10 and 50 are furnished with suction passages 102d, 103d, 503b to admit flowing of the fluid sucked into the working chambers 31, 32, 71, while the rotary members 41, 42, 81 are provided with suction communication passages 411, 421, 811 to make the working chambers 31, 32, 71 communicate to the suction passages 102d, 103d, 503b.

Description

  The present invention relates to a compressor in which a rotating member rotates in contact with an inner peripheral surface.

  Conventionally, in this type of compressor, by providing a port groove extending in the rotation direction of the rotor on the inner peripheral surface, the passage area of the fluid to the working chamber (the area of the passage through which the fluid sucked into the working chamber flows) It is known to ensure

  For example, Patent Document 1 describes a yoke vane type compressor having three vanes in which a port groove extending from the suction port to the maximum suction rotation angle is provided on the inner peripheral surface.

JP 2001-165082 A

  FIG. 12A is a cross-sectional view showing the yoke vane type compressor of Patent Document 1. Here, when the rotation angle of the rotor 90 when the suction starts is 0 °, the rotation angle of the rotor 90 when the compression is started is referred to as a compression start angle θa.

  When the port groove 92 is provided on the inner peripheral surface 91 as shown in FIG. 12A, although the passage area of the fluid to the working chamber is increased, the compression is not started until the vane 93 passes through the port groove 92. The compression start angle θa increases (compression is delayed).

  When the compression start angle θa is increased, there is a problem that the suction volume is reduced in a yoke vane type compressor having only one vane. This will be described with reference to FIGS. 12 (b) and 12 (c) show a yoke vane type compressor having only one vane without a port groove on the inner peripheral surface 91, and FIG. 12 (d) shows a yoke vane having only one vane. A type compressor having an inner peripheral surface 91 provided with a port groove 92 is shown.

  As shown in FIG. 12B, when no port groove is provided on the inner peripheral surface 91, compression starts when the vane 93 passes through the suction port 94. Therefore, since the compression start angle θa is relatively small, the suction volume Va (the volume of the hatched portion) is relatively large.

  However, as shown in FIG. 12C, when the port groove is not provided on the inner peripheral surface 91, the passage width of the fluid sucked into the working chamber is reduced, so that the passage area of the fluid to the working chamber is also reduced. Become.

  On the other hand, as shown in FIG. 12D, when the port groove 92 is provided on the inner peripheral surface 91, although the passage area of the fluid to the working chamber is increased, the compression is performed until the vane 93 passes through the port groove 92. Since it is not started, the compression start angle θa is increased (compression is delayed).

  As a result, the suction volume Va (volume of the hatched portion) is reduced as compared with that in FIG. In order to make the suction volume Va equivalent to that shown in FIG. 12B, it is necessary to increase the size of the entire compressor.

  In addition, when the compression start angle θa is increased, the compression angle (the angle at which the rotor rotates from the start of compression to the end of compression) is decreased, which causes a problem of rapid compression and increased torque fluctuation.

  The present invention has been made in view of the above points, and it is an object of the present invention to ensure a fluid passage area to a working chamber without providing a port groove on an inner peripheral surface.

In order to achieve the above object, in the invention described in claim 1, an inner peripheral surface forming member (102, 103, 503) for forming an inner peripheral surface (102b, 103b, 503a) having a predetermined shape;
Rotating members (41, 42, 81) rotating in contact with the inner peripheral surfaces (102b, 103b, 503a);
Partition members (43, 44, 83) that partition the working chambers (31, 32, 71) formed between the inner peripheral surfaces (102b, 103b, 503a) and the rotating members (41, 42, 81). Prepared,
A suction passage (102d, 103d, 503b) through which fluid sucked into the working chamber (31, 32, 71) flows is formed in the inner peripheral surface forming member (102, 103, 503).
The rotating members (41, 42, 81) are formed with suction communication passages (411, 421, 811) that connect the working chambers (31, 32, 71) and the suction passages (102d, 103d, 503b). It is characterized by that.

  According to this, the working chamber (31, 32, 71) and the suction passage (102d, 103d, 503b) communicate with each other via the suction communication passage (411, 421, 811) of the rotating member (41, 42, 81). Therefore, the area of the passage through which the fluid sucked into the working chamber (31, 32, 71) flows can be secured by the suction communication passage (411, 421, 811). For this reason, the passage area of the fluid to the working chamber can be secured without providing a port groove on the inner peripheral surface.

According to a second aspect of the present invention, in the compressor according to the first aspect, the opposed surface forming member (101, 504a) that forms the opposed surface (101a, 504a) facing the axial end surface of the rotating member (41, 81). 504),
The suction communication passages (411, 811) open to the axial end surfaces of the rotating members (41, 81),
The opposed surface forming members (101, 504) are formed with opposed surface side suction communication passages (101d, 504d) that open to the opposed surfaces (101a, 504a) and communicate with the suction passages (102d, 503b).
The suction communication passages (411, 811) are characterized in that they communicate with the suction passages (102d, 503b) via the opposing surface side suction communication passages (101d, 504d).

  According to a third aspect of the present invention, in the compressor according to the second aspect, when the rotating member (41, 42, 81) rotates, the suction communication path (411, 811) and the opposing surface side suction communication path ( 101d and 504d) are switched between communication and blocking.

  According to this, the configuration can be simplified as compared with the case where a dedicated mechanism for switching communication and blocking between the suction communication passages (411, 811) and the opposed surface side suction communication passages (101d, 504d) is provided.

  According to a fourth aspect of the present invention, in the compressor according to the second or third aspect, the suction communication path (411, 811) is formed in an arc shape along the outer edge of the rotating member (41, 42, 81). It is characterized by being.

According to a fifth aspect of the present invention, in the compressor according to the fourth aspect, the one end portion (411a, 811a) of the suction communication passage (411, 811) rotates relative to the partition member (43, 44, 83). Located on the front side in the rotational direction of the members (41, 42, 81),
The other end portions (411b, 811b) of the suction communication passages (411, 811) are located behind the partition members (43, 44, 83) in the rotation direction of the rotation members (41, 42, 81). It is characterized by that.

  According to a sixth aspect of the present invention, in the compressor according to the fifth aspect, the other end (411b, 811b) of the suction communication passage (411, 811) is an outer peripheral surface of the rotating member (41, 42, 81). It is characterized by having an opening.

  According to the seventh aspect of the present invention, in the compressor according to the sixth aspect, the other end portions (411b, 811b) of the suction communication passages (411, 811) are located in the vicinity of the partition members (43, 44, 83). It is located.

According to an eighth aspect of the present invention, in the compressor according to any one of the first to seventh aspects, the inner peripheral surface (102b, 103b), the rotating member (41, 42), the partition member (43, 44). , And a plurality of working chambers (31, 32),
Among the plurality of rotating members (41, 42), one rotating member (41) has a rotational phase advanced than the other rotating members (42).
When the working chamber (31) formed by one rotating member (41) among the plurality of working chambers (31, 32) is an upstream working chamber,
The inner peripheral surface forming member (10) includes, from the upstream working chamber (31), the other working chambers (32) that are compressing fluid after completion of the suction stroke among the plurality of working chambers (31, 32). A discharge passage (105a) leading to is formed.

  According to this, since the fluid is compressed in the plurality of working chambers (31, 32), fluctuations in the shaft torque can be suppressed to a small level. Moreover, since the fluid is compressed in cooperation with the upstream working chamber (31) whose rotational phase is advanced and the other working chamber (32) whose rotational phase is delayed, the axial torque in each working chamber (31, 32). The fluctuation characteristics of can be made different. For this reason, since generation | occurrence | production of the peak of the shaft torque in synthetic | combination shaft torque can be suppressed, low torque fluctuation and low fluctuation frequency can be made compatible (refer FIG. 5 mentioned later).

  In addition, since the working chambers (31, 32) and the suction passages (102d, 103d) communicate with each other via the suction communication passages (411, 421) of the rotating members (41, 42), the compression starts while securing the suction area. It is possible to reduce the angle (accelerate compression) (see FIG. 9 described later).

  For this reason, since generation | occurrence | production of the peak of the axial torque in synthetic | combination axial torque can be suppressed easily, low torque fluctuation and low fluctuation frequency can be made compatible easily (refer FIG. 10 mentioned later).

In the invention according to claim 9, in the compressor according to claim 8, when the other working chamber (32) is a downstream working chamber,
A mechanism (41, 42) is provided that closes the discharge passage (105a) when the internal pressure of the upstream working chamber (31) is lower than the internal pressure of the downstream working chamber (32).

  Thereby, it can prevent that the refrigerant | coolant of a downstream working chamber (32) flows back into an upstream working chamber (31) through a discharge channel (105a).

According to a tenth aspect of the present invention, the compressor according to the ninth aspect includes a plate-shaped partition member (105) that partitions the upstream working chamber (31) and the downstream working chamber (32),
The upstream working chamber (31) and the downstream working chamber (32) are arranged adjacent to each other in the axial direction of the upstream working chamber (31),
The discharge passage (105a) is formed in the partition member (105),
The mechanism for closing the discharge passage (105a) is constituted by a rotating member (41, 42).

  According to this, compared with the case where the mechanism for exclusive use for closing a discharge channel (105a) is provided, a structure can be simplified.

In the invention according to claim 11, in the compressor according to claim 10, the rotating members (41, 42) are rotors that rotate in contact with the inner peripheral surfaces (102 b, 103 b),
The partition members (43, 44) are vanes that protrude from the outer peripheral surface of the rotor (41, 42) and come into contact with the inner peripheral surfaces (102b, 103b),
The end of the discharge passage (105a) on the upstream working chamber (31) side overlaps with the rotor (41) that forms the upstream working chamber (31),
The end of the discharge passage (105a) on the downstream working chamber (32) side overlaps with the rotor (42) forming the downstream working chamber (32),
The rotor (41) forming the upstream working chamber (31) is formed with an upstream communication passage (41b) for communicating the discharge passage (105a) with the upstream working chamber (31).
The rotor (42) forming the downstream working chamber (32) is formed with a downstream communication passage (42b) for communicating the discharge passage (105a) with the downstream working chamber (32). .

In the invention described in claim 12, in the compressor described in claim 11, the upstream communication path (41b) is on the partition member (105) side of the rotor (41) forming the upstream working chamber (31). Composed of grooves formed on the end face of
The downstream communication path (42b) is characterized by a groove formed on an end surface of the rotor (42) forming the downstream working chamber (32) on the partition member (105) side.

  Thereby, the process of the communicating path (41b, 42b) with respect to a rotor (41, 42) can be performed easily.

According to a thirteenth aspect of the present invention, in the compressor according to any one of the first to tenth aspects, the rotating member (41, 42, 81) is inscribed in the inner peripheral surface (102b, 103b, 503a). A rotating rotor,
The partition members (43, 44, 83) are vanes that protrude from the outer peripheral surface of the rotor (41, 42, 91) and come into contact with the inner peripheral surfaces (102b, 103b, 503a).

In the invention according to claim 14, in the compressor according to any one of claims 11 to 13, the inner peripheral surface (102b, 103b) has a circular shape in cross section,
The rotating members (43, 44) are rotors that rotate eccentrically with respect to the inner peripheral surfaces (102b, 103b). Thus, the present invention is applicable to a yoke vane type compressor.

In the invention according to claim 15, in the compressor according to any one of claims 11 to 13, the inner peripheral surface (503a) has an elliptical cross section,
The rotating member (81) is a rotor that rotates concentrically with respect to the inner peripheral surface (503a). Thus, the present invention can also be applied to a Bosch vane type compressor.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a mimetic diagram of the refrigeration cycle for vehicles in a 1st embodiment. It is sectional drawing of the compressor in 1st Embodiment. It is explanatory drawing explaining the mechanism which opens and closes the discharge channel | path of FIG. It is CC sectional drawing and DD sectional drawing of FIG. 4 is a graph showing changes in bore internal pressure, bore capacity, and shaft torque in the first embodiment. It is sectional drawing of the compressor in 2nd Embodiment. It is explanatory drawing explaining a motion of the rotor side suction | inhalation communicating path in FIG. It is a graph which shows the expansion area and expansion area change in 2nd Embodiment. It is a figure explaining the suction area increase effect in 2nd Embodiment. It is a figure explaining the reduction effect of the shaft torque fluctuation frequency in 2nd Embodiment. It is sectional drawing of the compressor in 3rd Embodiment. It is sectional drawing of the compressor in a prior art.

(First embodiment)
Hereinafter, the first embodiment will be described. This embodiment shown in FIGS. 1-5 is embodiment as a reference example which shows the basic composition of the compressor used as the application object of this invention.

  FIG. 1 is a schematic diagram of a refrigeration cycle for a vehicle to which the compressor of this embodiment is applied. The compressor (compressor) 1 sucks and discharges refrigerant (fluid). The condenser (heat radiator) 2 condenses the gas-phase refrigerant discharged from the compressor 1. The decompressor 3 decompresses the refrigerant that has flowed out of the condenser 2. The evaporator 4 is a decompressor, and evaporates the liquid-phase refrigerant decompressed by the decompressor 3. The gas-phase refrigerant flowing out of the evaporator 4 is sucked into the compressor 1.

  FIG. 2 is a cross-sectional view of the compressor 1. The compressor 1 is a two-cylinder yoke vane compressor, and includes a housing 10 (inner peripheral surface forming member) that forms two cylinders and a shaft 11 that is inserted into the housing 10.

  In the example of FIG. 2, the housing 10 includes four divided housing members 101, 102, 103, 104 divided in the axial direction (left-right direction in FIG. 2A) and the divided housing members 102, 103, 104 mutually. The two partition plates 105 and 106 sandwiched between the two are fastened and fixed with bolts (not shown). The divided housing members 101 to 104 and the partition plates 105 and 106 are made of aluminum.

  Of the four divided housing members 101 to 104, circular housing holes 102a and 103a are formed through the axial direction in the divided housing members 102 and 103 disposed on the center side in the axial direction. Therefore, the divided housing members 102 and 103 form inner peripheral surfaces 102b and 103b having a circular cross section (a circular cross section).

  On the other hand, a flat surface 101a that closes the circular hole 102a of the divided housing member 102 is formed in the divided housing member 101 arranged on one end side in the axial direction (the left end side in FIG. 2A).

  Thereby, between the divided housing members 101 to 103 and the partition plates 105 and 106, two spaces 21 and 22 having a circular cross section are formed in series in the axial direction. In the present embodiment, the inner diameter dimensions and volumes of the two cross-sectional circular spaces 21 and 22 are the same.

  The two cross-sectional circular spaces 21 and 22 constitute working chambers 31 and 32 that suck in and compress the refrigerant. Therefore, the partition plates 105 and 106 serve as partition members that partition the two working chambers 31 and 32.

  Of the four divided housing members 101 to 104, the divided housing member 104 arranged on the other axial end side (left end side in FIG. 2A) has one axial end side (left end side in FIG. 2A). A recess 104a is formed to open toward the surface.

  Accordingly, a space 23 is formed between the divided housing member 104 and the partition plate 106. The space 23 constitutes a discharge chamber into which the refrigerant compressed in the circular spaces 21 and 22, that is, the working chambers 31 and 32, is discharged.

  The shaft 11 passes through the non-central portions of the three circular sectional spaces 21 and 22 and the partition plates 105 and 106. Both end portions of the shaft 11 are rotatably supported by the housing 10 via bearings 12 and 13.

  The split housing member 101 is formed with a hole 101c for connecting one end of the shaft 11 (the left end in FIG. 2A) to a shaft driving means (not shown). A lip seal 14 for preventing refrigerant leakage is disposed inside the hole 101c.

  In this example, since the engine for driving the vehicle is used as the shaft driving means, a pulley (not shown) and an electromagnetic clutch (not shown) to which the driving force from the engine is transmitted are provided on one end side of the shaft 11. Are connected. An electric motor may be used as the shaft driving means.

  Disc-shaped rotors 41 and 42 (rotating members) connected to the shaft 11 are arranged in each of the two circular sectional spaces 21 and 22.

  The rotors 41 and 42 have outer diameters smaller than the inner diameters of the cross-sectional circular spaces 21 and 22, and the central part thereof is connected to the shaft 11. The outer diameter dimension of the rotors 41 and 42 is the distance between the center of the shaft 11 and the portion (hereinafter referred to as the closest part) closest to the shaft 11 among the inner peripheral surfaces of the cross-sectional circular spaces 21 and 22. Are set to be the same. Therefore, the rotors 41 and 42 can rotate while inscribed in the closest portions of the cross-sectional circular spaces 21 and 22. In other words, the rotors 41 and 42 are eccentrically rotated in an inscribed state with respect to the inner peripheral surfaces 102b and 103b having a circular cross section. In the present embodiment, the outer dimensions of the rotors 41 and 42 are the same.

  Working chambers 31 and 32 are formed between the inner peripheral surfaces 102b and 103b and the rotors 41 and 42 to suck in and compress the refrigerant. Hereinafter, for convenience of explanation, the working chamber 31 on one end side in the axial direction is referred to as a first stage working chamber, and the working chamber 32 on the other end side in the axial direction is referred to as a second stage working chamber.

  Concave portions 41 a and 42 a that are recessed toward the inside of the rotors 41 and 42 are formed on the outer peripheral surfaces of the rotors 41 and 42. The recesses 41 a and 42 a are formed in a groove shape over the entire axial length of the rotors 41 and 42.

  Plate-like vanes 43 and 44 (partition members) are slidably inserted into the recesses 41a and 42a. In the recesses 41a and 42a, springs (not shown) for biasing the vanes 43 and 44 toward the inner peripheral surfaces 102b and 103b are arranged.

  Due to the urging force of a spring (not shown), the vanes 43 and 44 come in and out of the outer peripheral surface of the rotors 41 and 42 according to the rotational positions of the rotors 41 and 42 and come into contact with the inner peripheral surfaces 102b and 103b. Therefore, the working chambers 31 and 32 are divided into two spaces by the vanes 43 and 44.

  Hereinafter, for convenience of explanation, the rotation angle of the rotors 41 and 42 when the vanes 43 and 44 come into contact with the closest portions of the inner peripheral surfaces 102b and 103b is defined as 0 ° (see FIG. 3A). In the present embodiment, the two rotors 41 and 42 are coupled to the shaft 11 so that the rotational phase difference between them is equal. That is, the rotational phase difference between the rotors 41 and 42 is set to 360 ° / 2 = 180 °.

  As shown in FIGS. 2B and 2C, the divided housing member 104 is formed with a suction port 15 for sucking the refrigerant (uncompressed refrigerant) flowing out from the evaporator 4. As shown in FIG. 2B, the divided housing member 102 is formed with a suction passage 102 d that supplies the refrigerant sucked from the suction port 15 to the working chamber 31.

  The suction passage 102d opens to the inner peripheral surface 102b. In this example, the arrangement position of the suction passage 102d is approximately 10 to 30 ° in terms of the rotation angle of the rotor 41 (see FIG. 3).

  As shown in FIG. 2C, the divided housing member 103 is also formed with a suction passage 103d similar to the suction passage 102d. The arrangement position and shape of the suction passage 103d are the same as those of the suction passage 102d.

  As shown in FIGS. 2A and 2B, the partition plate 105 is formed with a discharge passage 105 a that connects the adjacent working chambers 31 and 32 to each other. In the present embodiment, three discharge passages 105a are formed. The arrangement positions of the three discharge passages 105a are about 270 °, about 310 °, and about 350 ° in terms of the rotation angle of the rotors 41 and 42 (see FIG. 3). The discharge passage 105 a is configured by a circular hole that penetrates the front and back of the partition plate 105.

  The discharge passage 105 a is opened and closed by the rotors 41 and 42. FIG. 3 is an explanatory diagram for explaining a mechanism for opening and closing the discharge passage 105a by the rotors 41 and 42, and shows the operation during one rotation of the rotors 41 and 42 at every rotation angle of 30 °.

  4A is a cross-sectional view taken along the line C-C in FIG. 3A, and illustrates a state where the discharge passage 105 a is closed by the rotors 41 and 42. FIG. 4B is a cross-sectional view taken along the line DD of FIG. 3I, and illustrates the state where the discharge passage 105 a is opened by the rotors 41 and 42.

  The rotor 41 is formed with a communication passage 41 b for communicating the discharge passage 105 a with the first stage working chamber 31. As shown in FIG. 4, the communication path 41 b is configured by a groove formed on the end surface of the rotor 41 on the partition plate 105 side. Specifically, the communication path 41b extends from the vicinity of the vane 43 to a circumferential groove extending in an arc shape in the circumferential direction of the rotors 41 and 42, and from the end on the vane 43 side of the circumferential groove toward the radially outer side. And a radial groove that extends and reaches the outer peripheral surface of the rotor 41, 42. The circumferential groove has a length that can be simultaneously superposed on two adjacent discharge passages 105a among the three discharge passages 105a.

  Similarly, a communication passage 42 b for communicating the discharge passage 105 a with the second stage working chamber 32 is formed in the rotor 42 so as to have the same shape and overlap as the communication passage 42 b of the rotor 41.

  In FIG. 3, the rotors 41 and 42 rotate in the clockwise direction. Hereinafter, for convenience of explanation, the rotation direction of the rotors 41 and 42 is simply referred to as a rotation direction. The rotation angle of the rotor 41 is referred to as a first rotation angle, and the rotation angle of the rotor 42 is referred to as a second rotation angle.

  When the rotation angle of the first stage shown in FIGS. 3A to 3H is 0 ° to 210 ° and the rotation angle of the second stage = 180 ° to 30 °, as illustrated in FIG. The discharge passage 105a is closed. That is, both end portions of the discharge passage 105 a are closed by the rotors 41 and 42.

  On the other hand, in the case where the first rotation angle = 240 ° to 330 ° and the second rotation angle = 60 ° to 150 ° shown in FIGS. Thus, the discharge passage 105a is opened. That is, since both ends of the discharge passage 105 a overlap with the communication passages 41 b and 42 b of the rotors 41 and 42, the discharge passage 105 a communicates with both working chambers 31 and 32.

  A final discharge passage (not shown) that connects the working chamber 32 and the discharge chamber 23 is formed in the partition plate 106 shown in FIG. The partition plate 106 is provided with a discharge valve (not shown) for opening and closing the final discharge passage. In the example of FIG. 2, a reed valve is used as a discharge valve, and a retainer 16 that regulates the opening degree of the discharge valve is disposed on the partition plate 106. The refrigerant in the discharge chamber 23 is discharged toward the condenser 2 from a discharge port (not shown) formed in the housing 10.

  Next, the operation in the above configuration will be described. When a shaft driving means (not shown) rotationally drives the shaft 11, the rotors 41 and 42 rotate. By the rotation of the rotors 41 and 42, the suction stroke and the compression stroke are repeatedly performed for each of the working chambers 31 and 32.

  Here, the suction stroke is a stroke in which the working chambers 31 and 32 are in communication with the suction passages 102d and 103d, and the uncompressed refrigerant from the suction passages 102d and 103d is sucked into the working chambers 31 and 32. The compression stroke is a stroke in which the working chambers 31 and 32 are disconnected from the suction passages 102d and 103d, and the refrigerant is compressed in the working chambers 31 and 32.

  As described above, the working chambers 31 and 32 are divided into two spaces by the vanes 43 and 44. The suction stroke is performed in one of the two spaces, and the compression stroke is performed in the other space.

  This will be specifically described with reference to FIG. Here, only the first-stage working chamber 31 will be described, but the basic operation of the second-stage working chamber 32 is the same.

  When the rotation angle at the first stage shown in FIGS. 3B to 3L is not 0 °, the counterclockwise direction side (counterclockwise direction side) with respect to the vane 43 of the two spaces formed in the working chamber 31 ) And a compression stroke is performed in another space, that is, a space positioned on the rotation direction side (clockwise direction side) with respect to the vane 43.

  The suction stroke starts when one space of the working chamber 31 communicates with the suction passage 102d. Then, when one space of the working chamber 31 is not in communication with the suction passage 102d, the compression stroke is started simultaneously with the end of the suction stroke.

  The end of the compression process is when the rotation angle at the first stage shown in FIG. That is, when the rotation angle of the first stage is 0 °, the vane 43 is pushed to the same plane as the outer peripheral surface of the rotor 41 by the closest portion of the inner peripheral surface of the circular space 21 or 22, so that the compression stroke is reduced. The volume of the space to be performed becomes zero, and the compression process ends.

  Thus, if attention is paid to one of the two spaces of the working chamber 31, the suction stroke and the compression stroke are performed for one cycle while the shaft 11 rotates twice. On the other hand, paying attention to the entire working chamber 31, since the suction stroke and the compression stroke are performed in parallel in the two spaces of the working chamber 31, the suction stroke and the compression stroke are performed once each time the shaft 11 rotates once. Will be.

  As described above, when the rotation angle at the first stage shown in FIGS. 3 (i) to (l) is 240 ° to 330 °, the discharge passage 105a is opened. As a result, the refrigerant compressed in the first stage working chamber 31 is discharged to the adjacent second stage working chamber 32 through the discharge passage 105a.

  As described above, in the second stage working chamber 32, the rotation phase is delayed by 180 ° with respect to the first stage working chamber 31, and therefore the second stage rotation angle when the discharge passage 105a is opened is 60 ° to 150 °. is there.

  Therefore, the refrigerant compressed in the first-stage working chamber 31 is supplied to the space in the compression stroke (the space being compressed after the suction stroke is completed) of the two spaces of the second-stage working chamber 32. As a result, in the second stage working chamber 32, the compressed refrigerant compressed in the first stage working chamber 31 is mixed with the uncompressed refrigerant supplied from the suction passage 102d and compressed.

  When the internal pressure of the second stage working chamber 32 reaches a predetermined pressure or higher, a discharge valve (not shown) is opened, so that the refrigerant compressed in the second stage working chamber 32 is discharged into the discharge chamber 23.

  Here, when the rotation angle of the second stage is 180 ° to 330 °, the rotation angle of the first stage working chamber 31 is 0 ° to 150 °. That is, in this case, the compression stroke is completed and the suction stroke is completed in the first stage working chamber 31, so the internal pressure in the first stage working chamber 31 is lower than the internal pressure in the second stage working chamber 32. .

  At this time, since the discharge passage 105a is closed as shown in FIGS. 3A to 3F, the refrigerant in the second stage working chamber 32 flows back to the first stage working chamber 31 through the discharge passage 105a. It is prevented.

  FIG. 5A is a graph showing fluctuations in the bore internal pressure (the internal pressure of the space during the compression stroke of the two spaces of the working chamber) in the above operation. The rotation angle on the horizontal axis in FIG. 5A indicates the rotation angle of the first stage. The broken line in FIG. 5A shows, as another reference example, fluctuations in bore internal pressure in a yoke vane type compressor having the same total capacity of the working chamber as in this embodiment and only one working chamber (one cylinder). Yes.

  Since the phase difference of 180 ° is set between the working chambers 31 and 32 as described above, the period during which the compression stroke is performed in the working chambers 31 and 32 is shifted by 180 °.

  Therefore, when the rotation angle is 0 ° to 180 °, the refrigerant is compressed only in the first stage working chamber 31, and when the rotation angle is 180 ° to 360 °, the refrigerant is compressed in the first and second stage working chambers 31 and 32. When the angle is 360 ° to 540 °, the refrigerant is compressed only in the second stage working chamber 32.

  When the rotation angle at which the refrigerant is compressed only in the first stage working chamber 31 = 0 ° to 180 °, the bore internal pressure increases as in the reference example.

  Among the rotation angles = 180 ° to 360 ° for compressing the refrigerant in the first and second stage working chambers 31 and 32, the discharge passage 105a is not yet opened at the rotation angle = 180 ° to 210 °, and the first stage operation is performed. The chamber 31 and the second stage working chamber 32 are isolated.

  For this reason, in the first stage working chamber 31, the bore internal pressure continues to rise as in the reference example, while in the second stage working chamber 32, only the uncompressed refrigerant is compressed, so the internal pressure in the second stage working chamber 32 is increased. It becomes lower than the internal pressure of the first stage working chamber 31.

  When the rotation angle is 210 ° to 360 °, the discharge passage 105a is opened so that the internal pressure of the first stage working chamber 31 and the internal pressure of the second stage working chamber 32 are equalized and then the first and second stage working chambers. The internal pressure of 31 and 32 will rise. For this reason, the rise in the bore internal pressure is moderate as compared with the reference example.

  The reason why the increase in the bore internal pressure stops after the rotation angle = about 360 ° is that the bore internal pressure reaches the valve opening pressure (predetermined pressure) of the discharge valve (not shown) and the discharge valve opens.

  As can be seen from FIG. 5A, in this embodiment, the compression stroke is completed at 540 ° (360 ° + 180 °), so that the bore internal pressure is increased compared to the reference example of one cylinder where the compression stroke is completed at 360 °. Can be relaxed. For this reason, torque fluctuation can be significantly reduced as compared with the reference example, and a primary component can be the main component in the torque fluctuation frequency. Here, the primary component means a component generated once with a rotation angle of 360 ° (rotor rotates once) as one cycle.

  This effect will be described in detail. FIG. 5B is a graph showing the fluctuation of the bore capacity (the capacity of the space during the compression stroke among the two spaces of the working chamber) for each of the working chambers 31 and 32 in the above operation. FIG. 5C is a graph showing the variation of the shaft torque in the above operation for each of the working chambers 31 and 32. FIG.5 (d) is the graph which showed the synthetic | combination axial torque which synthesize | combined the axial torque of each working chamber 31 and 32 in FIG.5 (c).

  Here, the axial torque is a torque necessary for driving the shaft 11, and is related to the amount of fluctuation of the bore capacity and the bore internal pressure. Specifically, the shaft torque increases when the bore capacity variation amount and the bore internal pressure are large.

  Therefore, the axial torques of the working chambers 31 and 32 shown in FIG. 5C are calculated from the bore internal pressure shown in FIG. 5A and the fluctuation characteristics of the bore capacities of the working chambers 31 and 32 shown in FIG. 5B. Furthermore, the combined shaft torque shown in FIG. 5 (d) can be obtained by combining the shaft torques of the working chambers 31 and 32 shown in FIG. 5 (c). The broken lines in FIGS. 5C and 5D indicate the shaft torque in the above-described reference example, that is, the one-cylinder yoke vane type compressor in which the total capacity of the working chamber is the same as that of the present embodiment.

  In this embodiment, as shown in FIG. 5 (c), the fluctuation characteristics of the shaft torque in the working chambers 31 and 32 are remarkably different from each other. Therefore, the fluctuation of the combined shaft torque is kept small as shown in FIG. 5 (d). In addition, it is possible to avoid the generation of a major peak in the compression stroke of each working chamber 31, 32 in the combined shaft torque, and to suppress the generation of the main peak only once per 360 ° rotation angle.

  For this reason, it is possible to achieve both the contradictory characteristics of low torque fluctuation and low fluctuation frequency. And by realizing the low torque fluctuation, the operation of the yoke vane compressor can be made smooth to reduce vibration. Further, by realizing the low fluctuation frequency, it is possible to suppress the resonance with various auxiliary machines arranged in the engine room.

  Further, according to the present embodiment, the discharge passage 105a is closed when the downstream working chamber 32 is in the suction stroke, so that the refrigerant discharged from the upstream working chamber 31 to the downstream working chamber 32 is in the downstream working chamber. It is possible to prevent backflow into the 32 suction passages 103d.

  Further, according to the present embodiment, the discharge passage 105a is closed when the internal pressure of the upstream working chamber 31 is lower than the internal pressure of the downstream working chamber 32, so that the refrigerant in the downstream working chamber 32 is discharged to the discharge passage. It is possible to prevent backflow into the upstream working chamber 31 through 105a.

  Moreover, according to the present embodiment, the discharge passage 105a is formed in the partition plate 106, and the communication passages 41b and 42b for connecting the discharge passage 105a to both the working chambers 31 and 32 are formed in the rotors 41 and 42. Therefore, the rotors 41 and 42 can open and close the discharge passage 105a at the complicated timing as described above. In other words, a mechanism for closing the discharge passage 105 a can be configured by the rotors 41 and 42.

  For this reason, compared with the case where a dedicated mechanism (for example, a valve mechanism) for closing the discharge passage 105a is provided, the configuration can be simplified, and as a result, the number of parts and the cost can be reduced.

  In particular, in the present embodiment, the discharge passage 105 a is configured by a simple circular hole that penetrates the partition plate 106, and the upstream communication passage 41 b and the downstream communication passage 42 b are grooves formed on the end surfaces of the rotors 41 and 42. Therefore, it is possible to easily process the discharge passage 105a and the two communication passages 41b and 42b.

  Further, since the upstream communication path 41b and the downstream communication path 42b have such a length that they can be simultaneously superposed on two adjacent discharge paths 105a among the three discharge paths 105a, the rotation angle is 210 ° to 360 °. The discharge passage 105a can be kept open over the entire range of °. For this reason, the refrigerant compressed in the first stage working chamber 31 can be stably discharged to the second stage working chamber 32.

  Further, since the upstream communication passage 41 b is formed in the vicinity of the vane 43, the refrigerant is discharged from the first stage working chamber 31 to the second stage working chamber 32 at the end of the compression stroke of the first stage working chamber 31. (Rotational angle: 360 °) can be performed satisfactorily.

  Further, according to the present embodiment, the two working chambers 31 and 32 cooperate to compress the refrigerant, so that the final refrigerant discharge is performed from the second-stage working chamber 32 and the first-stage operation is performed. Not done from chamber 31. Therefore, only one discharge valve (not shown) and one discharge chamber 23 are required. Therefore, for example, two (a plurality of) working chambers compress the refrigerant independently of each other, so that the number of parts is reduced as compared with a case where two (a plurality of) discharge chambers and a plurality of discharge chambers are required. Cost reduction and size reduction can be achieved.

(Second Embodiment)
In the second embodiment, with respect to the compressor 1 of the first embodiment, the rotor side suction communication paths 411 and 421 (suction communication paths) and the housing side suction communication paths 101d and 106a (opposing surface side suction communication paths). Has been added.

  The rotor side suction communication path 411 is formed in the rotor 41, and the rotor side suction communication path 421 is formed in the rotor 42. The housing side suction communication path 101 d is formed in the divided housing member 101, and the housing side suction communication path 106 a is formed in the partition plate 106.

  The rotor side suction communication path 411 and the housing side suction communication path 101 d constitute a refrigerant path for allowing the refrigerant to flow into the first stage working chamber 31. Similarly, the rotor-side suction communication passage 421 and the housing-side suction communication passage 106a constitute a refrigerant passage for allowing the refrigerant to flow into the second-stage working chamber 32.

  Since the structure of the rotor side suction communication path 421 and the housing side suction communication path 106a is the same as the structure of the rotor side suction communication path 411 and the housing side suction communication path 101d, the rotor side suction communication path 411 and the housing side suction communication will be described below. The structure of the communication path 101d will be described, and the description of the structure of the rotor side suction communication path 421 and the housing side suction communication path 106a will be omitted.

  The rotor-side suction communication passage 411 is formed in a groove shape on an end surface of the rotor 41 on the divided housing member 101 side (a flat surface on one end side in the axial direction). In this example, the rotor side suction communication passage 411 is formed in an arc shape (C shape) along the outer edge of the rotor 41.

  One end portion 411 a of the rotor side suction communication passage 411 is located on the front side in the rotational direction of the rotor 41 with respect to the vane 43 (clockwise direction side in FIG. 6B), and inside the outer edge of the rotor 41. It is terminated. That is, one end 411 a of the rotor side suction communication passage 411 is not in communication with the first stage working chamber 31.

  The other end portion 411b of the rotor side suction communication passage 411 is located behind the vane 43 in the rotation direction of the rotor 41 (counterclockwise direction side in FIG. 6B) and reaches the outer edge of the rotor 41. Thus, the outer surface of the rotor 41 is open. In other words, the other end 411 b of the rotor side suction communication passage 411 is in communication with the first stage working chamber 31.

  The housing-side suction communication passage 101d is formed in a groove shape on a flat surface 101a (opposing surface) that faces the axial end surface of the rotor 42 of the divided housing member 101 (opposing surface forming member), and one end thereof is divided. The housing member 102 communicates with the suction passage 102d, and the other end can communicate with the rotor-side suction communication passage 411.

  As shown in FIGS. 7A and 7B, when the rotation angle of the rotor 41 is 0 ° to 45 °, the rotor side suction communication passage 411 does not communicate (polymerize) with the housing side suction communication passage 101d. Therefore, the uncompressed refrigerant from the suction passage 102d is directly sucked into the working chambers 31 and 32, and is sucked into the working chambers 31 and 32 through the housing side suction communication passage 101d and the rotor side suction communication passage 411. Absent.

  As shown in FIGS. 7C to 7H, when the rotation angle of the rotor 41 is 90 ° to 315 °, the rotor side suction communication passage 411 communicates (polymerizes) with the housing side suction communication passage 101d. Therefore, the uncompressed refrigerant from the suction passage 102d is directly sucked into the working chambers 31 and 32, and is sucked into the working chambers 31 and 32 through the housing side suction communication passage 101d and the rotor side suction communication passage 411.

  By making the rotor side suction communication passages 411 and 421 into an arc shape, the suction passage can be secured up to a rotation angle close to 360 °. As shown in FIG. 8B, the angle at which the communication between the rotor-side suction communication passages 411 and 421 and the housing-side suction communication passage 101d ends (shuts down) (the suction communication groove communication end angle) is as shown in FIG. It is desirable that the Δ expansion area (the amount of change in the expansion area with respect to the rotation angle) shown in FIG.

  As shown in FIG. 9, in the present embodiment in which the housing side suction communication passage 101d and the rotor side suction communication passage 411 are provided, a comparative example in which the housing side suction communication passage 101d and the rotor side suction communication passage 411 are not provided. In comparison, the refrigerant suction area can be increased.

  That is, in the comparative example, the suction area = suction gap × bore length, whereas in this embodiment, the suction area = suction gap × bore length + suction groove area. The area can be increased. As shown in FIG. 9B, the suction gap is the dimension of the gap between the outlet of the suction passage 102d and the outer peripheral surface of the rotor 41, and the bore length is shown in FIG. 9C. Thus, the axial dimension of the working chamber 31 is shown. In FIG. 9B, cross-sectional hatching is omitted for convenience of illustration.

  Therefore, in this embodiment, since the suction area can be secured even if the compression start angle is advanced, both performance and downsizing can be achieved.

  Furthermore, in this embodiment, since the compression start angle can be reduced (compression is accelerated) while securing the suction area, it is easy to use the primary component as the main component in the torque fluctuation frequency. That is, as shown in FIG. 10, when the compression start angle is 45 °, since the compression start is slow, the discharge timing from the first stage to the second stage is delayed, and the bore pressure in the first stage is too high. As a result, the torque fluctuation becomes the characteristic of the secondary component instead of the characteristic of the primary component as intended, whereas when the compression start angle is 20 °, the compression start is quick and the first stage. The discharge timing from the first stage to the second stage becomes earlier, and the bore pressure in the first stage becomes smaller. As a result, the torque fluctuation becomes the characteristic of the primary component as intended.

(Third embodiment)
In the second embodiment, an example in which the present invention is applied to a yoke vane compressor has been described. However, in the third embodiment, the present invention is applied to a Bosch vane compressor. A Bosch vane type compressor compresses a refrigerant by rotating while a rotor contacts an inner peripheral surface having an elliptical cross section.

  Below, a different part from the said 2nd Embodiment is demonstrated, and description is abbreviate | omitted about the part similar to the said 2nd Embodiment.

  As shown in FIG. 11A, the Bosch vane type compressor of this embodiment has one cylinder. The housing 50 (inner peripheral surface forming member) includes a front housing 501, a rear housing 502, a rotor housing 503, and two side plates 504 and 505.

  The rotor housing 503 is formed with an inner peripheral surface 503a that forms an elliptical hole. The two side plates 504 and 505 are formed with flat surfaces that close the oval holes of the rotor housing 503.

  As a result, a space 61 having an elliptical cross section is formed between the rotor housing 503 and the side plates 504 and 505. The space 61 having an elliptical cross section constitutes a working chamber 71 that sucks and compresses the refrigerant.

  The shaft 51 passes through the center of the space 61 having an elliptical cross section. A disk-shaped rotor 81 (rotating member) connected to the shaft 51 is disposed in the space 61 having an elliptical cross section.

  The rotor 81 has the same outer diameter as that of the short-diameter dimension of the elliptical section space 61 and is connected to the shaft 51 at the center. Therefore, the rotor 81 can rotate concentrically with respect to the space 61 having the elliptical cross section while being inscribed in the inner peripheral surface 503a of the rotor housing 503 at the short diameter portion of the elliptical space 61. Two crescent-shaped working chambers 71 are formed between the inner peripheral surface 503 a and the rotor 81.

  Two recesses 81a are formed on the outer peripheral surface of the rotor 81, and a plate-like vane 83 (partition member) is slidably inserted into and retracted from each of the two recesses 81a. The vane 83 divides the working chamber 71 into two.

  The rotor side suction communication path 811 (suction communication path) is formed on the end surface (flat surface) of the rotor 81 on the side plate 504 side. Two rotor-side suction communication passages 811 are formed corresponding to the two working chambers 71. In this example, the rotor side suction communication passage 811 is formed in an arc shape (C shape) along the outer edge of the rotor 81.

  One end portion 811 a of the rotor side suction communication passage 811 is located on the front side in the rotation direction of the rotor 81 with respect to the one vane 83 (clockwise direction side in FIG. 11B), and is more than the outer edge of the rotor 81. Terminates inside. That is, one end portion 811 a of the rotor side suction communication passage 811 is not in communication with the working chamber 71.

  The other end portion 811 b of the rotor side suction communication path 811 is located on the rear side in the rotation direction of the rotor 81 (counterclockwise direction side in FIG. 11B) with respect to the other vane 83. Reaches the outer peripheral surface of the rotor 81. That is, the other end portion 811 b of the rotor side suction communication passage 811 communicates with the working chamber 71.

  The housing-side suction communication passage 504d (opposing surface-side suction communication passage) has two rotor-side intakes on a flat surface 504a (opposing surface) that faces the axial end surface of the rotor 81 in the side plate 504 (opposing surface forming member). Two communication passages 811 are formed corresponding to one end thereof, and one end portion thereof communicates with the suction passage 503b of the rotor housing 503, and the other end portion thereof can communicate with the rotor side suction communication passage 811.

  FIG. 11B shows a state in which the rotor-side suction communication passage 811 communicates (polymerizes) with the housing-side suction communication passage 504d. In this state, the uncompressed refrigerant from the suction passage 503b is directly sucked into the working chamber 71 and is sucked into the working chamber 71 through the housing side suction communication passage 504d and the rotor side suction communication passage 811.

  FIG. 11C shows a state where the rotor side suction communication passage 811 is not in communication (polymerization) with the housing side suction communication passage 504d. In this state, the uncompressed refrigerant from the suction passage 503b is only directly sucked into the working chamber 71 and is not sucked into the working chamber 71 through the housing side suction communication passage 504d and the rotor side suction communication passage 811.

  Also in this embodiment, the same effect as the second embodiment can be obtained.

(Other embodiments)
(1) In the second and third embodiments, the rotor side suction communication passages 411 and 811 are formed in a groove shape on the end surfaces of the rotors 41 and 81, but the rotor side suction communication passages 411 and 811 are the rotor 41, 81 may be formed in a hole shape.

  Similarly, in the second and third embodiments, the housing-side suction communication passages 101d and 504d are formed in a groove shape on the flat surfaces 101a and 504a of the housings 10 and 50, but the housing-side suction communication passages 101d and 504d. May be formed in the housing 10, 50 in the shape of a hole.

  In this case, for example, a part of the rotor side suction communication passages 411 and 811 opens at the end surfaces of the rotors 41 and 81, and a part of the housing side suction communication passages 101d and 504d is a flat surface 101a and 504a of the housings 10 and 50. If the opening is open, the rotor side suction communication passages 411 and 811 and the housing side suction communication passages 101d and 504d can communicate with each other.

  The housing side suction communication passages 101d and 504d are not essential, and the rotor side suction communication passages 411 and 811 may be in direct communication with the suction passages 102d and 503b.

  (2) The first and second embodiments are merely examples of the arrangement and shape of the discharge passages 105a and 106a, and the arrangement and shape of the discharge passages 105a and 106a can be variously modified.

  (3) In the first and second embodiments, the discharge passages 105a and 106a are opened and closed by the rolling pistons 31 to 33 or the rotors 41 and 42. However, the discharge passages 105a and 106a are opened by a valve mechanism (for example, a lead). It may be opened and closed by a valve or a solenoid valve.

  For example, the discharge passage may be formed in the housing, and the discharge passage may be opened and closed by a valve mechanism. Further, the discharge passage may be formed in the vane, and the discharge passage may be opened and closed by the vane in and out. Further, the discharge passage may be formed in the shaft, and the discharge passage may be opened and closed by the rotation of the shaft.

  (4) In the first and second embodiments, the inner peripheral surfaces 102b and 103b are formed by the housings 10 and 50. However, the cylinder block is accommodated in the housing, and the inner peripheral surfaces 102b and 103b are formed in the cylinder block. You may make it do.

  (5) In the second embodiment, the present invention is applied to a two-cylinder yoke vane type compressor. However, the present invention is not limited to this, and the present invention is also applied to a yoke vane type compressor having three or more cylinders. The invention can be applied.

  (6) In the third embodiment, an example in which the present invention is applied to a one-cylinder Bosch vane compressor has been described. However, the present invention is not limited to this, and a Bosch vane compressor having two or more cylinders is used. The present invention is also applicable.

  (7) In the third embodiment, the example in which the present invention is applied to the Bosch vane type compressor having the inner peripheral surface of the elliptical cross section is shown. However, the cross sectional shape of the inner peripheral surface is not a strict elliptical shape. Alternatively, it may have a special profile shape that is substantially elliptical.

  (8) The compressor to which the present invention is applied is not limited to a yoke vane type compressor or a Bosch vane type compressor, and various rotary types in which a rotating member rotates in contact with an inner peripheral surface of a predetermined shape. The present invention can be widely applied to compressors.

  (9) In each of the above embodiments, an example in which the present invention is applied to a compressor that compresses a refrigerant in a vehicle refrigeration cycle has been described. However, the present invention is not limited to this, and the present invention is applied to a compressor that compresses various fluids. The invention is widely applicable.

31, 32 Working chamber 41, 42 Rotor (rotating member)
43, 44 Vane (partition member)
101 Divided housing member (opposing surface forming member)
102, 103 Split housing member (inner peripheral surface forming member)
102b, 103b Inner peripheral surface 105 Partition plate (partition member)
105a Discharge passage 105b Through-hole portion 105c Groove portion 102d Suction passage 411 Rotor side suction communication passage (suction communication passage)
101a Flat surface (opposite surface)
101d Housing side suction communication path (opposite surface side suction communication path)

Claims (15)

An inner peripheral surface forming member (102, 103, 503) for forming an inner peripheral surface (102b, 103b, 503a) of a predetermined shape;
Rotating members (41, 42, 81) rotating in contact with the inner peripheral surfaces (102b, 103b, 503a);
Partition members (43, 44, 83) that partition the working chambers (31, 32, 71) formed between the inner peripheral surfaces (102b, 103b, 503a) and the rotating members (41, 42, 81). And
A suction passage (102d, 103d, 503b) through which fluid sucked into the working chamber (31, 32, 71) flows is formed in the inner peripheral surface forming member (102, 103, 503).
The rotating members (41, 42, 81) are formed with suction communication passages (411, 421, 811) that connect the working chambers (31, 32, 71) and the suction passages (102d, 103d, 503b). The compressor characterized by being made. An opposing surface forming member (101, 504) that forms an opposing surface (101a, 504a) facing the axial end surface of the rotating member (41, 81);
The suction communication passages (411, 811) open to the axial end surface,
The opposed surface forming members (101, 504) are formed with opposed surface side suction communication passages (101d, 504d) that open to the opposed surfaces (101a, 504a) and communicate with the suction passages (102d, 503b). ,
The compressor according to claim 1, wherein the suction communication path (411, 811) communicates with the suction path (102d, 503b) via the opposed surface side suction communication path (101d, 504d). .   As the rotating member (41, 42, 81) rotates, the communication between the suction communication path (411, 811) and the opposed surface side suction communication path (101d, 504d) is switched. The compressor according to claim 2.   The compressor according to claim 2 or 3, wherein the suction communication passage (411, 811) is formed in an arc shape along an outer edge of the rotating member (41, 42, 81). One end portions (411a, 811a) of the suction communication passages (411, 811) are located on the front side in the rotation direction of the rotation members (41, 42, 81) with respect to the partition members (43, 44, 83). ,
The other end portions (411b, 811b) of the suction communication passages (411, 811) are located on the rear side in the rotation direction of the rotating member (41, 42, 81) with respect to the partition member (43, 44, 83). The compressor according to claim 4, wherein the compressor is provided.   6. The compression according to claim 5, wherein the other end portions (411b, 811b) of the suction communication passages (411, 811) are opened in an outer peripheral surface of the rotating member (41, 42, 81). Machine.   The compressor according to claim 6, wherein the other end portions (411b, 811b) of the suction communication passages (411, 811) are located in the vicinity of the partition members (43, 44, 83). . A plurality of sets of the inner peripheral surface (102b, 103b), the rotating member (41, 42), the partition member (43, 44), and the working chamber (31, 32);
Among the plurality of rotating members (41, 42), one rotating member (41) has a rotational phase advanced than the other rotating members (42),
When the working chamber (31) formed by the one rotating member (41) among the plurality of working chambers (31, 32) is an upstream working chamber,
In the inner peripheral surface forming member (10), from the upstream-side working chamber (31), the other operation during compression of the fluid after completion of the suction stroke among the plurality of working chambers (31, 32). The compressor according to any one of claims 1 to 7, wherein a discharge passage (105a) reaching the chamber (32) is formed. When the other working chamber (32) is a downstream working chamber,
9. A mechanism (41, 42) for closing the discharge passage (105a) when an internal pressure in the upstream working chamber (31) is lower than an internal pressure in the downstream working chamber (32). The compressor described in 1. A plate-shaped partition member (105) that partitions the upstream working chamber (31) and the downstream working chamber (32);
The upstream working chamber (31) and the downstream working chamber (32) are arranged adjacent to each other in the axial direction of the upstream working chamber (31),
The discharge passage (105a) is formed in the partition member (105),
The compressor according to claim 9, wherein the mechanism for closing the discharge passage (105a) is constituted by the rotating member (41, 42). The rotating members (41, 42) are rotors that rotate in contact with the inner peripheral surfaces (102b, 103b),
The partition members (43, 44) are vanes that protrude from the outer peripheral surface of the rotor (41, 42) and come into contact with the inner peripheral surfaces (102b, 103b),
An end of the discharge passage (105a) on the upstream working chamber (31) side overlaps with the rotor (41) forming the upstream working chamber (31),
An end of the discharge passage (105a) on the downstream working chamber (32) side overlaps with the rotor (42) forming the downstream working chamber (32),
The rotor (41) forming the upstream working chamber (31) is formed with an upstream communication passage (41b) for communicating the discharge passage (105a) with the upstream working chamber (31).
The rotor (42) forming the downstream working chamber (32) is formed with a downstream communication passage (42b) for communicating the discharge passage (105a) with the downstream working chamber (32). The compressor according to claim 10. The upstream communication passage (41b) is configured by a groove formed on an end surface of the rotor (41) forming the upstream working chamber (31) on the partition member (105) side,
The downstream communication passage (42b) is configured by a groove formed on an end surface of the rotor (42) forming the downstream working chamber (32) on the partition member (105) side. The compressor according to claim 11. The rotating member (41, 42, 81) is a rotor that rotates inscribed in the inner peripheral surface (102b, 103b, 503a),
The partition member (43, 44, 83) is a vane that protrudes and protrudes from the outer peripheral surface of the rotor (41, 42, 91) and contacts the inner peripheral surface (102b, 103b, 503a). The compressor according to any one of claims 1 to 10. The inner peripheral surface (102b, 103b) has a circular cross section.
The compressor according to any one of claims 11 to 13, wherein the rotating member (43, 44) is a rotor that rotates eccentrically with respect to the inner peripheral surface (102b, 103b). The inner peripheral surface (503a) has an elliptical cross section,
The compressor according to any one of claims 11 to 13, wherein the rotating member (81) is a rotor that rotates concentrically with respect to the inner peripheral surface (503a).

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