JP2011117435A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To compatibly achieve low torque fluctuation and a low fluctuation frequency. <P>SOLUTION: A compressor includes a housing 10 formed with inner circumferential surfaces 101b, 102b having round cross sections, disk shape rolling pistons 31, 32 eccentrically rotating along the inner circumferential surface, and a plurality of pairs of vanes 51, 52 moving out of and into the inner circumferential surface and abutting on the rolling pistons. Working chambers 41, 42 in which a suction stroke for sucking fluid and a compression stroke for compressing fluid sucked in the suction stroke are carried out are formed between each of the inner circumferential surface and each of the rolling piston. A rolling piston out of the plurality of rolling pistons is in an advanced rotation phase as compared to other rolling pistons. A discharge passage 105a leading to another working chamber in which fluid after completion of the suction stroke is compressed from an upstream side working chamber is formed in the housing, the upstream side working chamber being a working chamber formed by the rolling piston in the advanced rotation phase. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a compressor having a plurality of cylinders.

  Conventionally, Patent Document 1 discloses a rolling piston compressor in which two cylinders are arranged side by side in the axial direction as this type of compressor. Here, the rolling piston compressor is a compression in which a rolling piston is disposed in a cylinder forming a circular inner peripheral surface, and the rolling piston compresses fluid by rotating eccentrically along the inner peripheral surface of the cylinder. It is a machine.

  In this prior art, the two cylinders operate independently of each other. That is, each of the two cylinders is provided with a suction port and a discharge port, and each cylinder has a suction port that sucks uncompressed refrigerant from the suction port and discharges compressed refrigerant from the discharge port. Parallel to the refrigerant flow.

  According to this prior art, since the refrigerant is compressed by two cylinders, it is possible to keep the fluctuation of the shaft torque low. That is, by shifting the phase between the two cylinders, fluctuations in shaft torque can be suppressed as compared with a rolling piston compressor having the same total capacity and only one cylinder. Here, the axial torque is a torque required to drive the shaft connected to the rolling piston.

JP 2005-127306 A

  However, if the configuration is such that two cylinders having different phases are simply provided in parallel as in the prior art described above, the fluctuation characteristics of the axial torque in each cylinder are the same. A shaft torque peak occurs. Specifically, the frequency of occurrence of a peak in the shaft torque is doubled compared to that with only one cylinder. For this reason, since the fluctuation frequency of the shaft torque becomes high, there is a concern about resonance with other parts.

  For example, when applied to a compressor of a refrigeration cycle for a vehicle, there is a concern about resonance with various auxiliary machines and the like arranged in the engine room together with the compressor.

  This problem occurs not only in a rolling piston compressor but also in a rotary compressor such as a yoke vane compressor. Here, a yoke vane type compressor is a cylinder in which a circular rotor is inscribed in a cylinder having a circular inner peripheral surface, and a plate-like vane is arranged in a slit formed in the rotor so that it can be projected and retracted. Is a compressor that compresses fluid by rotating the rotor around its central axis in a state where the rotor is in contact with the inner peripheral surface of the cylinder. A rotary compressor has a rotating member and a partition member arranged in a cylinder having an inner peripheral surface of a predetermined shape, and compresses fluid in a working chamber formed between the inner peripheral surface, the rotary member, and the partition member. It is a compressor that performs.

  In view of the above points, an object of the present invention is to achieve both low torque fluctuation and low fluctuation frequency.

In order to achieve the above object, in the invention according to claim 1, the inner peripheral surface forming member (10, 60) for forming the inner peripheral surface (101b, 102b, 602b, 603b) having a predetermined shape;
A rotating member (31, 32, 91, 92) that rotates in contact with the inner peripheral surface (101b, 102b, 602b, 603b);
Plural sets of partition members (51, 52, 93, 94) that partition the space formed between the inner peripheral surface (101b, 102b, 602b, 603b) and the rotating member (31, 32, 91, 92) Prepared,
Each inner peripheral surface (101b, 102b, 602b, 603b), rotating member (31, 32, 91, 92) and partition member (51, 52, 93, 94) in the inner peripheral surface forming member (10, 60) Are formed working chambers (41, 42, 81, 82) in which a suction stroke for sucking fluid and a compression stroke for compressing fluid sucked in the suction stroke are performed,
Among the plurality of rotating members (31, 32, 91, 92), one rotating member (31, 91) has a rotational phase advanced than the other rotating members (32, 92).
When the working chamber (41, 81) formed by one rotating member (31, 91) among the plurality of working chambers (41, 42, 81, 82) is an upstream working chamber,
The inner peripheral surface forming member (10, 60) compresses fluid from the upstream working chamber (41, 81) after completion of the suction stroke among the plurality of working chambers (41, 42, 81, 82). Discharge passages (105a, 605a) reaching other working chambers (42, 82) are formed.

  According to this, since the fluid is compressed in the plurality of working chambers (41, 42, 81, 82), fluctuations in the shaft torque can be suppressed to a small level. In addition, since the fluid is compressed in cooperation with the upstream working chamber (41, 81) whose rotational phase is advanced and the other working chamber (42, 82) whose rotational phase is delayed, each working chamber (41, 42) is compressed. , 81, 82) can vary the variation characteristics of the shaft torque. 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 and FIG. 6 mentioned later).

In the invention according to claim 2, in the compressor according to claim 1, when the other working chamber (42, 82) is a downstream working chamber,
Provided with a mechanism (31, 32, 91, 92) for closing the discharge passage (105a, 605a) when the internal pressure of the upstream working chamber (41, 81) is lower than the internal pressure of the downstream working chamber (42, 82). It is characterized by.

  Thereby, it is possible to prevent the refrigerant in the downstream working chamber (42, 82) from flowing back to the upstream working chamber (41, 81) through the discharge passage (105a, 605a).

According to a third aspect of the present invention, in the compressor according to the second aspect, the upstream working chamber (41, 81) and the downstream working chamber (42, 82) are arranged in the upstream working chamber (41, 81). Arranged next to each other in the axial direction,
The inner peripheral surface forming members (10, 60) have plate-like partition portions (105, 605) that partition the upstream working chamber (41, 81) and the downstream working chamber (42, 82),
The discharge passage (105a, 605a) is formed in the partition (105, 605),
The mechanism for closing the discharge passages (105a, 605a) is constituted by rotating members (31, 32, 91, 92).

  According to this, a structure can be simplified compared with the case where the mechanism for exclusive use for closing a discharge channel | path (105a, 605a) is provided.

In the invention according to claim 4, in the compressor according to any one of claims 1 to 3, the inner peripheral surface (101b, 102b) has a circular cross section,
The rotating members (31, 32) are disk-shaped rolling pistons that rotate eccentrically along the inner peripheral surfaces (101b, 102b),
The partition members (51, 52) are vanes that protrude from the inner peripheral surfaces (101b, 102b) and come into contact with the rolling pistons (31, 32).

  Thereby, in the rolling piston type compressor, the effect of the invention described in claims 1 to 3 can be obtained.

In the invention according to claim 5, in the compressor according to claim 3, the inner peripheral surface (101b, 102b) has a circular cross section.
The rotating members (31, 32) are disk-shaped rolling pistons that rotate eccentrically along the inner peripheral surfaces (101b, 102b),
The partition members (51, 52) are vanes that protrude from the inner peripheral surfaces (101b, 102b) and come into contact with the rolling pistons (31, 32),
The upstream working chamber (41) and the downstream working chamber (42) are arranged adjacent to each other in the axial direction of the upstream working chamber (41),
The inner peripheral surface forming member (10) has a plate-like partition (105) that partitions the upstream working chamber (41) and the downstream working chamber (42),
The discharge passage (105a) is formed in the partition (105),
The opening range with respect to the partition part (105) is different between the end part on the upstream working chamber (41) side and the end part on the downstream working chamber (42) side in the discharge passage (105a). .

  Thereby, in the rolling piston compressor, the effect of the invention described in claim 3 can be obtained.

  According to a sixth aspect of the present invention, in the compressor according to the fifth aspect, the discharge passage (105a) includes a through-hole portion (105b) extending parallel to the thickness direction of the partition portion (105) and a through-hole portion. The hole (105b) includes a groove (105c) extending from the end of the upstream working chamber (41) along the plate surface of the partition (105).

  According to this, for example, the discharge passage (105a) with respect to the partition portion (105) is compared with the case where the discharge passage (105a) is configured with a hole extending obliquely with respect to the thickness direction of the partition portion (105). Can be easily performed.

According to a seventh aspect of the present invention, in the compressor according to any one of the first to third aspects, the inner peripheral surface (602b, 603b) has a circular cross section,
The rotating members (91, 92) are rotors that rotate in contact with the inner peripheral surfaces (602b, 603b),
The partition members (93, 94) are vanes that protrude from the outer peripheral surface of the rotor (91, 92) and come into contact with the inner peripheral surfaces (602b, 603b).

  Thereby, in the yoke vane type compressor, the effect of the invention described in claims 1 to 3 can be obtained.

In the invention according to claim 8, in the compressor according to claim 3, the inner peripheral surface (602b, 603b) has a circular cross section,
The rotating members (91, 92) are rotors that rotate in contact with the inner peripheral surfaces (602b, 603b),
The partition members (93, 94) are vanes that protrude from the outer peripheral surface of the rotor (91, 92) and come into contact with the inner peripheral surfaces (602b, 603b),
The upstream working chamber (81) and the downstream working chamber (82) are arranged adjacent to each other in the axial direction of the upstream working chamber (81),
The inner peripheral surface forming member (60) has a plate-like partition (605) that partitions the upstream working chamber (81) and the downstream working chamber (82),
The discharge passage (605a) is formed in the partition portion (605),
The end of the discharge passage (605a) on the upstream working chamber (81) side overlaps with the rotor (91) forming the upstream working chamber (81),
The end of the discharge passage (605a) on the downstream working chamber (82) side overlaps with the rotor (92) forming the downstream working chamber (82),
The rotor (91) forming the upstream working chamber (81) is formed with an upstream communication passage (91b) that communicates the discharge passage (605a) with the upstream working chamber (81).
The rotor (92) forming the downstream working chamber (82) is formed with a downstream communication passage (92b) for communicating the discharge passage (605a) with the downstream working chamber (82). .

  Thereby, in the yoke vane type compressor, the effect of the invention described in claim 3 can be obtained.

According to the ninth aspect of the present invention, in the compressor according to the eighth aspect, the upstream communication path (91b) is on the partition (605) side of the rotor (91) forming the upstream working chamber (81). Composed of grooves formed on the end face of
The downstream side communication path (92b) is configured by a groove formed on an end surface of the rotor (92) forming the downstream side working chamber (82) on the partition part (605) side.

  Thereby, the process of the communicating path (91b, 92b) with respect to a rotor (91, 92) can be performed easily.

In the invention according to claim 10, in the compressor according to any one of claims 1 to 9, when the other working chambers (42, 82) are downstream working chambers,
The maximum volume of the downstream working chamber (42, 82) is smaller than the maximum volume of the upstream working chamber (41, 81).

  Thus, by appropriately setting the volume of each working chamber (41, 42, 81, 82), it is possible to optimize the internal pressure characteristics and further reduce the torque fluctuation.

  According to an eleventh aspect of the present invention, in the compressor according to any one of the first to ninth aspects, the rotating member (31, 32,) that forms a plurality of working chambers (41, 42, 81, 82). 91, 92) is characterized in that the rotational phase difference between them is non-uniform.

  Thus, by appropriately setting the phase difference between the working chambers (41, 42, 81, 82), it is possible to optimize the internal pressure characteristics and further reduce the torque fluctuation.

  In the present invention, when the number of working chambers, that is, the number of rotating members is n, the rotational phase difference between the rotating members is set to a value of 360 ° / n, the “rotating member” The rotational phase difference between the rotating members is equal. "When the rotation phase difference is set to a value different from 360 ° / n, the rotational phase difference between the rotating members is non-uniform.

  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 BB sectional drawing and CC sectional drawing of FIG. It is a graph which shows the change of the bore internal pressure and bore capacity in a 1st embodiment. It is a graph which shows the change of the shaft torque in a 1st embodiment. It is explanatory drawing explaining the mechanism which opens and closes the discharge channel | path in 2nd Embodiment. It is sectional drawing of the compressor in 3rd Embodiment. It is sectional drawing of the compressor in 4th Embodiment. It is sectional drawing of the compressor in 5th Embodiment. It is explanatory drawing explaining the mechanism which opens and closes the discharge passage of FIG. It is FF sectional drawing of FIG. 11, and GG sectional drawing. It is a graph which shows the change of the bore internal pressure in 5th Embodiment, a bore capacity | capacitance, and a shaft torque. It is sectional drawing of the compressor in 6th Embodiment. It is sectional drawing of the compressor in 7th Embodiment.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic diagram of a vehicle refrigeration cycle to which a compressor of the present invention 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 three-cylinder rolling piston compressor, and includes a housing (inner peripheral surface forming member) 10 that forms a cylinder, 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 divided housing members 101, 102, 103, The three partition plates 105, 106, and 107 sandwiched between 104 are fastened and fixed with bolts (not shown). The divided housing members 101 to 104 and the partition plates 105 to 107 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 (predetermined shape).

  On the other hand, the divided housing member 101 arranged on one end side in the axial direction (the left end side in FIG. 2A) has a circular concave portion arranged coaxially with the circular holes 102a and 103a of the divided housing members 102 and 103. 101a is formed so as to open toward the other end in the axial direction (the right end in FIG. 2A). Therefore, the divided housing member 101 forms an inner peripheral surface 101b having a circular cross section.

  Thereby, between the divided housing members 101 to 103 and the partition plates 105 to 107, three spaces 21, 22, and 23 having a circular cross section are formed in series in the axial direction. In the present embodiment, the three circular sectional spaces 21 to 23 have the same inner diameter and volume.

  The three cross-sectional circular spaces 21 to 23 constitute working chambers 41, 42, and 43 that suck in and compress the refrigerant. Therefore, the partition plates 105 and 106 serve as a partition portion that partitions the three working chambers 41 to 43.

  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 24 is formed between the divided housing member 104 and the partition plate 107. The space 24 constitutes a discharge chamber into which the refrigerant compressed in the circular cross-section spaces 21 to 23, that is, the working chambers 41 to 43 is discharged.

  The shaft 11 passes through the central part of the three circular sectional spaces 21 to 23 and the partition plates 105 to 107. 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 rolling pistons (rotating members) 31, 32, and 33 connected to the shaft 11 are disposed in each of the three cross-sectional circular spaces 21 to 23.

  The rolling pistons 31 to 33 have outer diameters smaller than the inner diameters of the cross-sectional circular spaces 21 to 23 and are connected to the shaft 11 so as to rotate eccentrically with respect to the cross-sectional circular spaces 21 to 23. Yes.

  And the part (henceforth a farthest part) farthest from a rotation center among rolling pistons 31-33 contact | abuts to the internal peripheral surfaces 101b, 102b, 103b of the cross-section circular space 21-23. Therefore, the rolling pistons 31 to 33 are eccentrically rotated along the inner peripheral surfaces 101b, 102b, and 103b of the circular sectional spaces 21 to 23.

  Working chambers 41, 42, and 43 for sucking and compressing refrigerant are formed between the circular spaces 21 to 23 and the rolling pistons 31 to 33, respectively. In the following, for convenience of explanation, the working chamber 41 on one axial side is the first-stage working chamber, the working chamber 42 in the center in the axial direction is the second-stage working chamber, and the working chamber 43 on the other end in the axial direction is the third-stage working. Say the room.

  In the present embodiment, the outer dimensions of the rolling pistons 31 to 33 are the same. In the present embodiment, the three rolling pistons 31 to 33 are connected to the shaft 11 so that the rotational phase difference between them is equal. That is, the rotational phase difference between the rolling pistons 31 to 33 is set to 360 ° / 3 = 120 °.

  The rolling pistons 31 to 33 include rotor portions 31a, 32a, and 33a fixed to the shaft 11, annular piston portions 31b, 32b, and 33b disposed on the outer peripheral side of the rotor portions 31a, 32a, and 33a, and a piston portion 31b. , 32b, 33b are configured with bearings (not shown) for rotatably supporting the rotor portions 31a, 32a, 33a.

  In the rolling pistons 31 to 33, the piston portions 31b, 32b, and 33b are not necessarily configured to be rotatable with respect to the rotor portions 31a, 32a, and 33a. The piston portions 31b, 32b, and 33b and the rotor portion 31a are not necessarily configured. 32a and 33a may be integrated into a single member.

  On the inner peripheral surfaces 101b, 102b, and 103b of the divided housing members 101 to 103, concave portions 101d, 102d, and 103d that are recessed toward the radially outer side (the upper side in FIG. 2) are formed. The recesses 101d, 102d, 103d are formed in a groove shape over the entire axial length of the inner peripheral surfaces 101b, 102b, 103b.

  Plate-like vanes (partition members) 51, 52, 53 are slidably inserted (can be projected and retracted) into the recesses 101d, 102d, 103d. In the recesses 101d, 102d, and 103d, springs 15, 16, and 17 that urge the vanes 51 to 53 toward the center of the circular sectional spaces 21 to 23 are arranged.

  Due to the urging force of the springs 15 to 17, the vanes 51 to 53 are projected and retracted from the inner peripheral surfaces 101b, 102b, and 103b according to the rotational positions of the rolling pistons 31 to 33, and the piston portions 31b, 32b of the rolling pistons 31 to 33, 33b. Therefore, the working chambers 41 to 43 are divided into two spaces by the vanes 51 to 53.

  Below, for convenience of explanation, the rotation angle of the rolling pistons 31 to 33 when the farthest part of the rolling pistons 31 to 33 contacts the vanes 51 to 53 is defined as 0 ° (see FIG. 3A).

  The split housing member 101 is formed with a suction port (not shown) for sucking the refrigerant (uncompressed refrigerant) flowing out from the evaporator 4. As shown in FIG. 2B, the divided housing member 101 is formed with a suction passage 101 e that supplies the refrigerant sucked from the suction port to the working chamber 41.

  The suction passage 101e is open to the inner peripheral surface 101b and is opened and closed by the rolling piston 31. In this example, the arrangement position of the suction passage 101e is about 30 ° in terms of the rotation angle of the rolling pistons 31 to 33 (see FIG. 3).

  The divided housing members 102 and 103 are also formed with suction passages 102e and 103e similar to the suction passage 101e. Since the arrangement positions and shapes of the suction passages 102e and 103e are the same as those of the suction passage 101e, only the reference numerals of the suction passages 102e and 103e are attached in parentheses in FIG. 2B to illustrate the suction passages 102e and 103e. Omitted.

  The partition plate 105 is formed with a discharge passage 105 a that allows the adjacent working chambers 41 and 42 to communicate with 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 angles of the rolling pistons 31 to 33 (see FIG. 3).

  Similarly to the partition plate 105, the partition plate 106 is also formed with a discharge passage 106 a that allows the adjacent working chambers 42 and 43 to communicate with each other. Since the arrangement position, shape, and the like of the discharge passage 106a are the same as those of the discharge passage 105a, only the reference numeral of the discharge passage 106a is given in parentheses in FIG. 2B, and the illustration of the discharge passage 106a is omitted.

  The discharge passage 105 a is opened and closed by the rolling pistons 31 and 32. Similarly, the discharge passage 106 a is opened and closed by the rolling pistons 32 and 33. FIG. 3 is an explanatory diagram for explaining a mechanism for opening and closing the discharge passage 105a by the rolling pistons 31 and 32, and shows an operation during one rotation of the rolling pistons 31 and 32 at every rotation angle of 30 °.

  4A is a cross-sectional view taken along the line BB in FIG. 3A, and illustrates a state where the discharge passage 105 a is closed by the rolling pistons 31 and 32. 4B is a cross-sectional view taken along the line C-C in FIG. 3H, and illustrates a state where the discharge passage 105 a is opened by the rolling pistons 31 and 32.

  The mechanism for opening and closing the discharge passage 106a is the same as the mechanism for opening and closing the discharge passage 105a shown in FIGS.

  The opening position (opening range) of the discharge passage 105a with respect to the partition plate 105 is different between one end and the other end. Specifically, as shown in FIG. 4, the discharge passage 105a includes a circular through-hole portion 105b extending parallel to the thickness direction of the partition plate 105, and the first-stage working chamber 41 of the through-hole portion 105b. It is comprised by the groove part 105c extended in a radial direction outer side along the plate | board surface of the partition plate 105 from the edge part of the side.

  In FIG. 3, the rolling pistons 31 to 33 rotate in the clockwise direction. Hereinafter, for convenience of explanation, the rotation direction of the rolling pistons 31 to 33 is simply referred to as a rotation direction. In addition, the rotation angle of the rolling piston 31 is referred to as a first-stage rotation angle, and the rotation angle of the rolling piston 32 is referred to as a second-stage rotation angle.

  When the rotation angle of the first stage shown in FIGS. 3A to 3E is 0 ° to 120 ° and the rotation angle of the second stage = 240 ° to 0 °, as illustrated in FIG. The discharge passage 105a is closed. That is, one end portion (end portion on the groove portion 105c side) of the discharge passage 105a is not blocked by the rolling piston 31, but the other end portion (end portion opposite to the groove portion 105c) of the discharge passage 105a is covered by the rolling piston 32. Since it is blocked, the discharge passage 105a is closed.

  On the other hand, when the first stage rotation angle = 150 ° to 330 ° and the second stage rotation angle = 30 ° to 210 ° shown in FIGS. Thus, the discharge passage 105a is opened. That is, since both ends of the discharge passage 105a are not blocked by the rolling pistons 31 and 32, the discharge passage 105a is opened.

  In the partition plate 107 shown in FIG. 2A, a final discharge passage (not shown) that connects the working chamber 43 and the discharge chamber 24 is formed. The partition plate 107 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 19 that regulates the opening degree of the discharge valve is disposed on the partition plate 107. The refrigerant in the discharge chamber 24 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 rolling pistons 31 to 33 rotate eccentrically. By the eccentric rotation of the rolling pistons 31 to 33, the suction stroke and the compression stroke are repeatedly performed for each of the working chambers 41 to 43.

  Here, in the suction stroke, the working chambers 41 to 43 are in communication with the suction passages 101e, 102e, and 103e, and the uncompressed refrigerant from the suction passages 101e, 102e, and 103e is sucked into the working chambers 41 to 43. It is. The compression stroke is a stroke in which the working chambers 41 to 43 are disconnected from the suction passages 101e, 102e, and 103e, and the refrigerant is compressed in the working chambers 41 to 43.

  As described above, the working chambers 41 to 43 are divided into two spaces by the vanes 51 to 53. 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. Although only the first stage working chamber 41 will be described here, the basic operation is the same for the second and third stage working chambers 42 and 43.

  When the rotation angle of the first stage shown in FIGS. 3B to 3L is not 0 °, the two spaces formed in the working chamber 41 are on the rotation direction side (clockwise direction side) with respect to the vane 51. The suction stroke is performed in the space that is located, and the compression stroke is performed in the other space, that is, the space that is located on the counter-rotation direction side (counterclockwise direction side) with respect to the vane 51.

  The suction stroke begins when one space of the working chamber 41 is in communication with the suction passage 101e. Then, when one space of the working chamber 41 is not in communication with the suction passage 101e, the compression stroke is started simultaneously with the completion 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 at the first stage is 0 °, the vane 51 is pushed to the outside of the working chamber 41 by the farthest part of the rolling piston 31, so that the volume of the space in which the compression stroke is performed becomes zero and the compression stroke Ends.

  Thus, if attention is paid to one of the two spaces of the working chamber 41, 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 41, since the suction stroke and the compression stroke are performed in parallel in the two spaces of the working chamber 41, the suction stroke and the compression stroke are performed once each time the shaft 11 rotates once. Will be.

  As described above, when the first stage rotation angle shown in FIGS. 3F to 3L is 150 ° to 330 °, the discharge passage 105a is opened. Accordingly, the refrigerant compressed in the first stage working chamber 41 is discharged to the adjacent second stage working chamber 42 through the discharge passage 105a.

  As described above, since the rotation phase of the second stage working chamber 42 is delayed by 120 ° with respect to the first stage working chamber 41, the second stage rotation angle when the discharge passage 105a is opened is 30 ° to 210 °. is there.

  For this reason, the refrigerant compressed in the first stage working chamber 41 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 42. As a result, in the second stage working chamber 42, the compressed refrigerant compressed in the first stage working chamber 41 is mixed with the uncompressed refrigerant supplied from the suction passage 102e and compressed.

  In the second stage working chamber 42, as in the first stage working chamber 41, the discharge passage 106 a is opened when the rotation angle is 150 ° to 330 °. Therefore, the refrigerant compressed in the second stage working chamber 42 is The liquid is discharged into the adjacent third stage working chamber 43 through the discharge passage 106a.

  Here, when the rotation angle of the second stage is 240 ° to 330 °, the rotation angle of the first stage working chamber 41 is 0 ° to 90 °. That is, in this case, in the first stage working chamber 41, the compression stroke is completed and the suction stroke is completed, so the internal pressure in the first stage working chamber 41 is lower than the internal pressure in the second stage working chamber 42. .

  At this time, since the discharge passage 105a is closed as shown in FIGS. 3A to 3D, the refrigerant in the second-stage working chamber 42 flows back to the first-stage working chamber 41 through the discharge passage 105a. It is prevented.

  Also in the third stage working chamber 43, the refrigerant compressed in the second stage working chamber 42 is supplied to the space in the compression stroke of the two spaces, as in the second stage working chamber 42. The compressed refrigerant compressed in the second stage working chamber 42 is mixed with the uncompressed refrigerant supplied from 103e and compressed.

  Similarly to the discharge passage 105a, the discharge passage 106a is closed when the internal pressure of the second stage working chamber 42 is lower than the internal pressure of the third stage working chamber 43. The refrigerant is prevented from flowing back to the second stage working chamber 42 through the discharge passage 106a.

  When the internal pressure of the third stage working chamber 43 reaches a predetermined pressure or higher, a discharge valve (not shown) is opened, so that the refrigerant compressed in the third stage working chamber 43 is discharged into the discharge chamber 24.

  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 a comparative example, fluctuations in bore internal pressure in a rolling piston compressor having a total working chamber capacity identical to that of the present embodiment and only one working chamber (one cylinder). .

  Since the phase difference of 120 ° is set between the working chambers 41 to 43 as described above, the period during which the compression stroke is performed in each of the working chambers 41 to 43 is shifted by 120 °.

  Therefore, when the rotation angle is 0 ° to 120 °, the refrigerant is compressed only in the first stage working chamber 41, and when the rotation angle is 120 ° to 240 °, the refrigerant is compressed and rotated in the first and second stage working chambers 41 and 42. When the angle is 240 ° to 360 °, the refrigerant is compressed in the first to third stage working chambers 41 to 43, and when the rotation angle is 360 ° to 480 °, the refrigerant is compressed and rotated in the second and third stage working chambers 42 and 43. When the angle is 480 ° to 600 °, the refrigerant is compressed only in the third stage working chamber 43.

  When the rotation angle at which the refrigerant is compressed only in the first stage working chamber 41 = 0 ° to 120 °, the bore internal pressure increases as in the comparative example.

  Among the rotation angles = 120 ° -240 ° for compressing the refrigerant in the first and second stage working chambers 41, 42, the discharge passage 105a is not yet opened at the rotation angle = 120 ° -150 °, and the first stage operation is performed. The chamber 41 and the second stage working chamber 42 are isolated from each other.

  For this reason, the bore internal pressure continues to rise in the first stage working chamber 41 as in the comparative example, while only the uncompressed refrigerant is compressed in the second stage working chamber 42, so the internal pressure in the second stage working chamber 42 is increased. It becomes lower than the internal pressure of the first stage working chamber 41.

  When the rotation angle is 150 ° to 240 °, the discharge passage 105a is opened, so that the internal pressure of the first stage working chamber 41 and the internal pressure of the second stage working chamber 42 are equalized, and then the first and second stage working chambers. The internal pressure of 41 and 42 will rise. For this reason, the increase in the bore internal pressure is moderate as compared with the comparative example.

  Among the rotation angles = 240 ° to 360 ° for compressing the refrigerant in the first to third operation chambers 41 to 43, the discharge passage 106a is not yet opened at the rotation angle = 240 ° to 270 °, so the third operation is performed. The internal pressure of the chamber 43 is lower than the internal pressure of the first and second stage working chambers 41 and 42.

  When the rotation angle is 270 ° to 360 °, the discharge passage 105a is opened, so that the internal pressure of the first and second stage working chambers 41 and 42 and the inner pressure of the third stage working chamber 43 are equalized to 1 to 3. The internal pressure of the stage working chambers 41 to 43 will increase. For this reason, the increase in bore internal pressure becomes more gradual than in the comparative example.

  The reason why the bore internal pressure stops increasing after the rotation angle = about 320 ° 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 600 ° (360 ° + 120 ° + 120 °), so that the bore internal pressure is compared with the comparative example of one cylinder where the compression stroke is completed at 360 °. Can be moderated. For this reason, torque fluctuation can be significantly reduced as compared with the comparative example, and the primary component can be the main component in the torque fluctuation frequency. Here, the primary component means a component that occurs once with a rotation angle of 360 ° (one rotation of the rolling piston) as one cycle.

  This effect will be described in detail. FIG. 5B is a graph showing fluctuations in the bore capacity (the capacity of the space during the compression stroke of the two spaces of the working chamber) in each of the working chambers 41 to 43 in the above operation. FIG. 6A is a graph showing the fluctuation of the shaft torque in the above operation for each of the working chambers 41 to 43. FIG. 6B is a graph showing a combined shaft torque obtained by combining the shaft torques of the working chambers 41 to 43 in FIG.

  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.

  Accordingly, the axial torques of the working chambers 41 to 43 shown in FIG. 6A are calculated from the bore internal pressure shown in FIG. 5A and the fluctuation characteristics of the bore capacities of the working chambers 41 to 43 shown in FIG. Further, the combined shaft torque shown in FIG. 6 (b) can be obtained by combining the shaft torques of the working chambers 41 to 43 shown in FIG. 6 (a). The broken lines in FIGS. 6A and 6B indicate the shaft torque in the comparative example, that is, the rolling piston type compressor having the same working chamber total capacity as that of the present embodiment and one cylinder.

  In this embodiment, as shown in FIG. 6A, the fluctuation characteristics of the shaft torque in each of the working chambers 41 to 43 are remarkably different from each other. Therefore, the fluctuation of the combined shaft torque is kept small as shown in FIG. 6B. In addition, it is possible to avoid the occurrence of a peak for each compression stroke of each working chamber 41 to 43 in the combined shaft torque, and to suppress the generation of the 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 implement | achieving a low torque fluctuation | variation, the action | operation of the compressor 1 can be made smooth and a vibration can be reduced. 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 passages 105a and 106a are closed when the downstream working chambers 42 and 43 are in the suction stroke, so that the discharge passages 105a and 106a are discharged from the upstream working chambers 41 and 42 to the downstream working chambers 42 and 43. It is possible to prevent the refrigerant from flowing back into the suction passages 102e and 103e of the downstream working chambers 42 and 43.

  Further, according to the present embodiment, the discharge passages 105a and 106a are closed when the internal pressure of the upstream working chambers 41 and 42 is lower than the internal pressure of the downstream working chambers 42 and 43. It is possible to prevent the refrigerants 42 and 43 from flowing back to the upstream working chambers 41 and 42 through the discharge passages 105a and 106a.

  Moreover, according to the present embodiment, the discharge passages 105a and 106a are formed in the partition plates 105 and 106, and the opening positions (opening ranges) of the discharge passages 105a and 106a are made different at one end and the other end. Therefore, the opening and closing of the discharge passages 105a and 106a at the complicated timing as described above can be performed by the rolling pistons 31 to 33. In other words, a mechanism for closing the discharge passages 105a and 106a can be configured by the rolling pistons 31 to 33.

  For this reason, compared with the case where a dedicated mechanism (for example, a valve mechanism) for closing the discharge passages 105a and 106a 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, in order to make the opening positions (opening ranges) of the discharge passages 105a and 106a different between the one end and the other end, the discharge passage 105a is formed with respect to the thickness direction of the partition plates 105 and 106. A through-hole portion 105b extending in parallel and a groove portion 105c extending along the plate surfaces of the partition plates 105 and 106 from one end portion of the through-hole portion 105b. For this reason, for example, compared with the case where the discharge passages 105a and 106a are configured with holes extending obliquely with respect to the thickness direction of the partition plates 105 and 106, the discharge passages 105a and 106a with respect to the partition plates 105 and 106 are formed. Processing can be performed easily.

In addition, according to the present embodiment, the three working chambers 41 to 43 cooperate to compress the refrigerant, so that the final refrigerant discharge is performed from the third-stage working chamber 43, The operation chambers 41 and 42 are not used. Therefore, only one discharge valve (not shown) and one discharge chamber 24 are required. Therefore, for example, three (plural) working chambers compress the refrigerant independently of each other, so that the number of parts and the number of discharge valves and discharge chambers are three (plural). Cost reduction and size reduction can be achieved.
(Second Embodiment)
In the first embodiment, all the discharge passages 105a are constituted by the through-hole portion 105b and the groove portion 105c. However, in the second embodiment, as shown in FIG. Only the discharge passage 105a is composed of a through-hole portion and a groove portion, and the remaining three discharge passages 105a are composed of only the through-hole portion.

According to the present embodiment, by changing the arrangement position of the discharge passage 105a with respect to the first embodiment, a part of the discharge passage 105a can be configured with only through holes. For this reason, the processing of the discharge passage 105a with respect to the partition plate 105 can be performed more easily.
(Third embodiment)
In the said 1st Embodiment, although the volume of the cross-sectional circular space 21-23, ie, the maximum volume of each working chamber 41-43, is the same, in this 3rd Embodiment, as shown in FIG. The volume of the circular spaces 21 to 23, that is, the maximum volume of each working chamber 41 to 43 gradually decreases from the first stage to the third stage.

Thus, by appropriately setting the volumes of the working chambers 41 to 43, it is possible to optimize the internal pressure characteristics and further reduce the torque fluctuation.
(Fourth embodiment)
In the first embodiment, the phase difference between the working chambers 41 to 43 is equal (120 °). However, in the fourth embodiment, as shown in FIG. The phase difference between them is non-uniform.

  Thus, by appropriately setting the phase difference between the working chambers 41 to 43, it is possible to optimize the internal pressure characteristics and further reduce the torque fluctuation.

Incidentally, the opening and closing of the discharge passages 105a and 106a in the present embodiment can be performed by the rolling pistons 31 to 33 as in the first embodiment. Moreover, it is preferable that the arrangement of the discharge passages 105a and 106a is appropriately changed according to the setting of the phase difference between the working chambers 41 to 43.
(Fifth embodiment)
In each of the above embodiments, an example in which the present invention is applied to a rolling piston compressor has been described. In the fifth embodiment, the present invention is applied to a yoke vane compressor.

  As shown in FIG. 10, the yoke vane compressor of the present embodiment includes a housing (inner peripheral surface forming member) 60 that forms two cylinders, and a shaft 61 that is inserted into the housing 60.

  In the example of FIG. 10, the housing 60 includes four divided housing members 601, 602, 603, and 604 divided in the axial direction (the left-right direction in FIG. 2A), and the divided housing members 602, 603, and 604. The two partition plates 605 and 606 sandwiched between the two are fastened and fixed with bolts (not shown). The divided housing members 601 to 604 and the partition plates 605 and 606 are made of aluminum.

  Of the four divided housing members 601 to 604, circular holes 602a and 603a are formed penetrating in the axial direction in the divided housing members 602 and 603 disposed on the center side in the axial direction. Accordingly, the divided housing members 602 and 603 form inner peripheral surfaces 602b and 603b having a circular cross section.

  On the other hand, a flat surface 601a that closes the circular hole 602a of the divided housing member 602 is formed in the divided housing member 601 that is disposed on one end side in the axial direction (the left end side in FIG. 2A).

  Thereby, between the divided housing members 601 to 603 and the partition plates 605 and 606, two spaces 71 and 72 having a circular cross section are formed in series in the axial direction. In the present embodiment, the two sectional circular spaces 71 and 72 have the same inner diameter and the same volume.

  The two cross-sectional circular spaces 71 and 72 constitute working chambers 81 and 82 that suck in and compress the refrigerant. Therefore, the partition plates 605 and 606 serve as a partition portion that partitions the two working chambers 81 to 82.

  Of the four divided housing members 601 to 604, the divided housing member 604 disposed on the other axial end side (left end side in FIG. 10A) has one axial end side (left end side in FIG. 10A). ) A recess 604a that opens to face.

  Accordingly, a space 73 is formed between the divided housing member 604 and the partition plate 606. The space 73 constitutes a discharge chamber into which the refrigerant compressed in the circular cross-section spaces 71 and 72, that is, the working chambers 81 and 82 is discharged.

  The shaft 61 passes through the non-central portion of the three circular sectional spaces 71 and 72 and the partition plates 605 and 606. Both end portions of the shaft 61 are rotatably supported by the housing 60 via bearings 62 and 63.

  The divided housing member 601 is formed with a hole 601c for connecting one end portion of the shaft 61 (the left end portion in FIG. 10A) to shaft driving means (not shown). A lip seal 64 for preventing refrigerant leakage is disposed inside the hole 601c.

  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 61. Are connected. An electric motor may be used as the shaft driving means.

  Disc-shaped rotors (rotating members) 91 and 92 connected to the shaft 61 are disposed in each of the two circular sectional spaces 71 and 72.

  The rotors 91 and 92 have outer diameters smaller than the inner diameters of the cross-sectional circular spaces 71 and 72, and the central parts thereof are connected to the shaft 11. The outer diameter dimension of the rotors 91 and 92 is the distance between the center of the shaft 11 and the part (hereinafter referred to as the closest part) closest to the shaft 11 among the inner peripheral surfaces of the cross-sectional circular spaces 71 and 72. Are set to be the same. Therefore, the rotors 91 and 92 can rotate while inscribed in the closest portions of the cross-sectional circular spaces 71 and 72. In the present embodiment, the outer dimensions of the rotors 91 and 92 are the same.

  Working chambers 81 and 82 for sucking and compressing the refrigerant are formed between the circular spaces 71 and 72 and the rotors 91 and 92. Hereinafter, for convenience of explanation, the working chamber 81 on one end side in the axial direction is referred to as a first stage working chamber, and the working chamber 82 on the other end side in the axial direction is referred to as a second stage working chamber.

  Concave portions 91 a and 92 a that are recessed toward the inside of the rotors 91 and 92 are formed on the outer peripheral surfaces of the rotors 91 and 92. The recesses 91a and 92a are formed in a groove shape over the entire axial length of the rotors 91 and 92.

  Plate-like vanes (partition members) 93 and 94 are slidably inserted into the recesses 91a and 92a. In the recesses 91a and 92a, springs (not shown) for biasing the vanes 93 and 94 toward the inner peripheral surfaces of the circular sectional spaces 71 and 72 are arranged.

  Due to the urging force of a spring (not shown), the vanes 93 and 94 protrude from the outer peripheral surface of the rotors 91 and 92 according to the rotational positions of the rotors 91 and 92, and come to the inner peripheral surfaces of the cross-sectional circular spaces 71 and 72. Abut. Therefore, the working chambers 81 and 82 are divided into two spaces by the vanes 93 and 94.

  Hereinafter, for convenience of explanation, the rotation angle of the rotors 91 and 92 when the vanes 93 and 94 come into contact with the closest portions of the circular sectional spaces 71 and 72 is defined as 0 ° (see FIG. 11A). . In the present embodiment, the two rotors 91 and 92 are coupled to the shaft 61 so that the rotational phase difference between them is equal. That is, the rotational phase difference between the rotors 91 and 92 is set to 360 ° / 2 = 180 °.

  As shown in FIGS. 10B and 10C, the split housing member 604 is formed with a suction port 65 for sucking the refrigerant (uncompressed refrigerant) flowing out from the evaporator 4. As shown in FIG. 10B, the divided housing member 602 is formed with a suction passage 602 d for supplying the refrigerant sucked from the suction port to the working chamber 81.

  The suction passage 602d opens on the inner peripheral surface 602b. In this example, the arrangement position of the suction passage 602d is about 10 to 30 ° in terms of the rotation angle of the rotor 91 (see FIG. 11).

  As shown in FIG. 10C, the divided housing member 603 is also formed with a suction passage 603d similar to the suction passage 602d. The arrangement position and shape of the suction passage 603d are the same as those of the suction passage 602d.

  As shown in FIGS. 10A and 10B, the partition plate 605 is formed with a discharge passage 605 a that allows the adjacent working chambers 81 and 82 to communicate with each other. In the present embodiment, three discharge passages 605a are formed. The arrangement positions of the three discharge passages 605a are about 270 °, about 310 °, and about 350 ° in terms of the rotation angles of the rotors 91 and 92 (see FIG. 11). The discharge passage 605a is formed by a circular hole that penetrates the front and back of the partition plate 605.

  The discharge passage 605a is opened and closed by the rotors 91 and 92. FIG. 11 is an explanatory diagram for explaining a mechanism for opening and closing the discharge passage 605a by the rotors 91 and 92. The operation during one rotation of the rotors 91 and 92 is shown at every rotation angle of 30 °.

  FIG. 12A is a cross-sectional view taken along line FF in FIG. 11A, and illustrates a state where the discharge passage 605 a is closed by the rotors 91 and 92. FIG. 12B is a GG cross-sectional view of FIG. 11I, and illustrates a state where the discharge passage 605 a is opened by the rotors 91 and 92.

  The rotor 91 is formed with a communication passage 91 b for communicating the discharge passage 605 a with the first working chamber 81. As illustrated in FIG. 12, the communication path 91 b is configured by a groove formed on the end surface of the rotor 91 on the partition plate 605 side. Specifically, the communication path 91b extends from the vicinity of the vane 93 to a circumferential groove extending in an arc shape in the circumferential direction of the rotors 91 and 92, and from the end on the vane 93 side of the circumferential groove toward the radially outer side. And a radial groove that extends and reaches the outer peripheral surfaces of the rotors 91 and 92. The circumferential groove has a length that can be simultaneously superposed on two adjacent discharge passages 605a among the three discharge passages 605a.

  Similarly, the rotor 92 is formed with a communication passage 92 b for communicating the discharge passage 605 a with the second working chamber 82 so as to have the same shape and overlap as the communication passage 92 b of the rotor 91.

  In FIG. 11, the rotors 91 and 92 rotate in the clockwise direction. Hereinafter, for convenience of explanation, the rotation direction of the rotors 91 and 92 is simply referred to as a rotation direction. The rotation angle of the rotor 91 is referred to as a first rotation angle, and the rotation angle of the rotor 92 is referred to as a second rotation angle.

  When the rotation angle of the first stage shown in FIGS. 11A to 11H is 0 ° to 210 ° and the rotation angle of the second stage = 180 ° to 30 °, as illustrated in FIG. The discharge passage 605a is closed. That is, both end portions of the discharge passage 605a are closed by the rotors 91 and 92.

  On the other hand, when the first stage rotation angle = 240 ° to 330 ° and the second stage rotation angle = 60 ° to 150 ° shown in FIGS. 11 (i) to 11 (l), examples are shown in FIG. 12 (b). Thus, the discharge passage 605a is opened. That is, since both ends of the discharge passage 105a overlap with the communication passages 91b and 92b of the rotors 91 and 92, the discharge passage 605a communicates with the first and second working chambers 81 and 82.

  In the partition plate 606 shown in FIG. 10A, a final discharge passage (not shown) that connects the working chamber 82 and the discharge chamber 73 is formed. On the partition plate 606, a discharge valve (not shown) for opening and closing the final discharge passage is disposed. In the example of FIG. 10, a reed valve is used as the discharge valve, and a retainer 66 that restricts the opening degree of the discharge valve is disposed on the partition plate 606. The refrigerant in the discharge chamber 73 is discharged toward the condenser 2 from a discharge port (not shown) formed in the housing 60.

  Next, the operation in the above configuration will be described. When a shaft driving means (not shown) drives the shaft 61 to rotate, the rotors 91 and 92 rotate. By the rotation of the rotors 91 and 92, the suction stroke and the compression stroke are repeatedly performed for each of the working chambers 81 and 82.

  Here, the suction stroke is a stroke in which the working chambers 81 and 82 are in communication with the suction passages 602d and 603d, and the uncompressed refrigerant from the suction passages 602d and 603d is sucked into the working chambers 81 and 82. The compression stroke is a stroke in which the working chambers 81 and 82 are disconnected from the suction passages 602d and 603d, and the refrigerant is compressed in the working chambers 81 and 82.

  As described above, the working chambers 81 and 82 are divided into two spaces by the vanes 93 and 94. 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 81 will be described, but the basic operation of the second-stage working chamber 82 is the same.

  When the rotation angle of the first stage shown in FIGS. 11B to 11L is not 0 °, the counterclockwise direction side (counterclockwise direction side) with respect to the vane 93 of the two spaces formed in the working chamber 81 ) 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 93.

  The suction stroke starts when one space of the working chamber 81 is in communication with the suction passage 602d. Then, when one space of the working chamber 81 is not in communication with the suction passage 602d, the compression stroke is started simultaneously with the end of the suction stroke.

  The end of the compression stroke is when the rotation angle at the first stage shown in FIG. That is, when the rotation angle at the first stage is 0 °, the vane 93 is pushed to the same plane as the outer peripheral surface of the rotor 91 by the closest portion of the inner peripheral surface of the circular space 71, 72, 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 81, the suction stroke and the compression stroke are performed for one cycle while the shaft 61 rotates twice. On the other hand, paying attention to the entire working chamber 81, since the suction stroke and the compression stroke are performed in parallel in the two spaces of the working chamber 81, the suction stroke and the compression stroke are performed once each time the shaft 61 rotates once. Will be.

  As described above, the discharge passage 605a is opened when the first rotation angle shown in FIGS. 11 (i) to 11 (l) is 240 ° to 330 °. Thus, the refrigerant compressed in the first stage working chamber 81 is discharged to the adjacent second stage working chamber 82 through the discharge passage 605a.

  As described above, since the rotation phase of the second stage working chamber 82 is delayed by 180 ° with respect to the first stage working chamber 81, the second stage rotation angle when the discharge passage 605a is opened is 60 ° to 150 °. is there.

  Therefore, the refrigerant compressed in the first-stage working chamber 81 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 82. As a result, in the second stage working chamber 82, the compressed refrigerant compressed in the first stage working chamber 81 is mixed with the uncompressed refrigerant supplied from the suction passage 602d and compressed.

  When the internal pressure of the second stage working chamber 82 reaches a predetermined pressure or higher, a discharge valve (not shown) is opened, so that the refrigerant compressed in the second stage working chamber 82 is discharged into the discharge chamber 73.

  Here, when the rotation angle of the second stage is 180 ° to 330 °, the rotation angle of the first stage working chamber 41 is 0 ° to 150 °. That is, in this case, in the first stage working chamber 81, the compression stroke is completed and the suction stroke is completed, so that the internal pressure in the first stage working chamber 81 is lower than the internal pressure in the second stage working chamber 82. .

  At this time, since the discharge passage 605a is closed as shown in FIGS. 11A to 11F, the refrigerant in the second-stage working chamber 82 flows back to the first-stage working chamber 81 through the discharge passage 605a. It is prevented.

  FIG. 13A 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. 13A indicates the rotation angle of the first stage. As a comparative example, the broken line in FIG. 13A shows fluctuations in bore internal pressure in a yoke vane type compressor having the same total capacity of the working chamber as that of the present embodiment and only one working chamber (one cylinder).

  As described above, since a phase difference of 180 ° is set between the working chambers 81 and 82, the period during which the compression stroke is performed in the working chambers 81 and 82 is shifted by 180 °.

  Therefore, when the rotation angle is 0 ° to 180 °, the refrigerant is compressed only in the first stage working chamber 81, and when the rotation angle is 180 ° to 360 °, the refrigerant is compressed and rotated in the first and second stage working chambers 81 and 82. When the angle is 360 ° to 540 °, the refrigerant is compressed only in the second stage working chamber 82.

  At the rotation angle = 0 ° to 180 ° at which the refrigerant is compressed only in the first stage working chamber 81, the bore internal pressure increases as in the comparative example.

  Of the rotation angles = 180 ° to 360 ° for compressing the refrigerant in the first and second stage working chambers 81 and 82, the discharge passage 605a is not yet opened at the rotation angle = 180 ° to 210 °, and the first stage operation is performed. The chamber 81 and the second stage working chamber 82 are isolated from each other.

  Therefore, in the first stage working chamber 81, the bore internal pressure continues to increase as in the comparative example, while in the second stage working chamber 82, only the uncompressed refrigerant is compressed, so the internal pressure in the second stage working chamber 82 is increased. It becomes lower than the internal pressure of the first stage working chamber 81.

  When the rotation angle is 210 ° to 360 °, the discharge passage 605a is opened, so that the internal pressure of the first stage working chamber 81 and the internal pressure of the second stage working chamber 82 are equalized, and then the first and second stage working chambers. The internal pressures 81 and 82 will increase. For this reason, the increase in the bore internal pressure is moderate as compared with the comparative example.

  The reason why the increase in 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. 13A, in this embodiment, the compression stroke is completed at 540 ° (360 ° + 180 °), so that the bore internal pressure is increased as compared with the one-cylinder comparative example in which the compression stroke is completed at 360 °. Can be relaxed. For this reason, torque fluctuation can be significantly reduced as compared with the comparative example, and the 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. 13B is a graph showing the fluctuation of the bore capacity (the capacity of the space during the compression stroke of the two spaces of the working chamber) for each of the working chambers 81 and 82 in the above operation. FIG. 13C is a graph showing the variation of the shaft torque in the operation for each of the operation chambers 81 and 82. FIG.13 (d) is the graph which showed the synthetic | combination axial torque which synthesize | combined the axial torque of each working chamber 81,82 in FIG.13 (c).

  Here, the axial torque is a torque necessary for driving the shaft 61, and is related to the variation amount 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 torque of each working chamber 81, 82 shown in FIG. 13 (c) is obtained from the bore internal pressure shown in FIG. 13 (a) and the fluctuation characteristics of the bore capacity of each working chamber 81, 82 shown in FIG. 13 (b). Furthermore, the combined shaft torque shown in FIG. 13 (d) can be obtained by combining the shaft torques of the working chambers 41 to 43 shown in FIG. 13 (c). The broken lines in FIGS. 13C and 13D show the shaft torque in the above comparative example, that is, the yoke vane type compressor having the same total capacity of the working chamber as that of the present embodiment and one cylinder.

  In the present embodiment, as shown in FIG. 13C, the fluctuation characteristics of the shaft torque in the working chambers 81 and 82 are significantly different from each other, so that the fluctuation of the combined shaft torque is kept small as shown in FIG. 13D. In addition, it is possible to avoid the generation of a major peak for each compression stroke of the working chambers 81 and 82 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 605a is closed when the downstream working chamber 82 is in the suction stroke, so that the refrigerant discharged from the upstream working chamber 81 to the downstream working chamber 82 is in the downstream working chamber. It is possible to prevent backflow into the suction passage 603d of 82.

  Further, according to the present embodiment, the discharge passage 605a is closed when the internal pressure of the upstream working chamber 81 is lower than the internal pressure of the downstream working chamber 82, so that the refrigerant in the downstream working chamber 82 is discharged from the discharge passage. It is possible to prevent backflow into the upstream working chamber 81 through 605a.

  Moreover, according to the present embodiment, the discharge passage 605a is formed in the partition plate 606, and the communication passage 91b for connecting the discharge passage 605a to the first and second working chambers 81 and 82 is connected to the rotors 91 and 92. , 92b are formed, the rotors 91, 92 can open and close the discharge passage 605a at the complicated timing as described above. In other words, a mechanism for closing the discharge passage 605a can be configured by the rotors 91 and 92.

  For this reason, compared with the case where a dedicated mechanism (for example, a valve mechanism) for closing the discharge passage 605a 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 605a is configured by a simple circular hole that penetrates the partition plate 606, and the upstream communication passage 91b and the downstream communication passage 92b are grooves formed on the end surfaces of the rotors 91 and 92. Therefore, it is possible to easily process the discharge passage 605a and the both communication passages 91b and 92b.

  Further, since the upstream communication passage 91b and the downstream communication passage 92b have such a length that they can be simultaneously superposed on two adjacent discharge passages 605a among the three discharge passages 605a, the rotation angle is 210 ° to 360 °. The discharge passage 605a can be kept open over the entire range of °. For this reason, the refrigerant compressed in the first stage working chamber 81 can be stably discharged to the second stage working chamber 82.

  Further, since the upstream side communication passage 91b is formed in the vicinity of the vane 93, the refrigerant is discharged from the first stage working chamber 81 to the second stage working chamber 82 at the end of the compression stroke of the first stage working chamber 81. (Rotational angle: 360 °) can be performed satisfactorily.

Further, according to the present embodiment, the two working chambers 81 and 82 cooperate to compress the refrigerant, so that the final refrigerant discharge is performed from the second-stage working chamber 82 and the first-stage operation is performed. It is not performed from the chamber 81. Therefore, only one discharge valve (not shown) and one discharge chamber 73 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.
(Sixth embodiment)
In the fifth embodiment, the volumes of the circular sectional spaces 71 and 72, that is, the maximum volumes of the working chambers 81 and 82 are the same. However, in the sixth embodiment, as shown in FIG. The volume of the circular spaces 71 and 72, that is, the maximum volume of the working chambers 81 and 82 is smaller in the second stage than in the first stage.

Thus, by appropriately setting the volumes of the working chambers 81 and 82, it is possible to optimize the internal pressure characteristics and further reduce torque fluctuations.
(Seventh embodiment)
In the fifth embodiment, the phase difference between the working chambers 81 and 82 is equal (180 °). However, in the seventh embodiment, as shown in FIG. The phase difference between them is non-uniform.

  Thus, by appropriately setting the phase difference between the working chambers 81 and 82, it is possible to optimize the internal pressure characteristics and further reduce the torque fluctuation.

  Incidentally, the opening and closing of the discharge passage 605a in the present embodiment can be performed by the rotors 91 and 92 as in the first embodiment. In addition, the arrangement of the discharge passage 605a is preferably changed as appropriate in accordance with the setting of the phase difference between the working chambers 81 and 82.

(Other embodiments)
The above embodiments are merely examples of the arrangement and shape of the discharge passages 105a, 106a, and 605a, and the arrangement and shape of the discharge passages 105a, 106a, and 605a can be variously modified.

  In each of the above embodiments, the discharge passages 105a, 106a, 605a are opened and closed by the rolling pistons 31-33 or the rotors 91, 92, but the discharge passages 105a, 106a, 605a are valve mechanisms (for example, reed valves). 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.

  In each of the above embodiments, the inner peripheral surfaces 101b, 102b, 103b, 602b, and 603b are formed by the housings 10 and 60. However, the cylinder block is accommodated in the housing, and the inner peripheral surfaces 101b, 102b, 103b, 602b, and 603b may be formed.

  In the first to fourth embodiments, an example in which the present invention is applied to a three-cylinder rolling piston compressor has been described. However, the present invention is not limited to this, and the rolling piston compression having two or more cylinders is not limited thereto. The present invention can be applied to a machine.

  In the fifth to seventh embodiments, the present invention is applied to a two-cylinder yoke vane type compressor. However, the present invention is not limited to this, and a yoke vane type compressor having three or more cylinders is not limited thereto. The present invention is also applicable.

  Further, the present invention can be applied to various rotary compressors such as a Bosch vane compressor. Here, the Bosch vane type compressor is a compressor in which the rotor rotates in contact with the inner peripheral surface having an elliptical cross section, and the vanes appear and disappear from the outer peripheral surface of the rotor. In the Bosch vane compressor, the cross-sectional shape of the inner peripheral surface may not be a strict elliptical shape, but may be a special profile shape that is substantially elliptical.

  Further, in each of the above embodiments, the example in which the present invention is applied to the compressor that compresses the refrigerant of the vehicle refrigeration cycle has been described. However, the present invention is not limited to this, and the present invention is widely applied to compressors that compress various fluids. The invention can be applied.

10 Housing (inner peripheral surface forming member)
31, 32 Rolling piston (rotating member)
51, 52 Vane (partition member)
41, 42 Working chamber 101b, 102b Inner peripheral surface 105 Partition plate (partition part)
105a Discharge passage 105b Through hole 105c Groove

Claims (11)

An inner peripheral surface forming member (10, 60) for forming an inner peripheral surface (101b, 102b, 602b, 603b) of a predetermined shape;
A rotating member (31, 32, 91, 92) rotating in contact with the inner peripheral surface (101b, 102b, 602b, 603b);
Partition members (51, 52, 93, 94) that partition the spaces formed between the inner peripheral surfaces (101b, 102b, 602b, 603b) and the rotating members (31, 32, 91, 92). With multiple sets,
In the inner peripheral surface forming members (10, 60), the inner peripheral surfaces (101b, 102b, 602b, 603b), the rotating members (31, 32, 91, 92), and the partition members (51, 52, 93, 94) are formed working chambers (41, 42, 81, 82) in which a suction stroke for sucking fluid and a compression stroke for compressing the fluid sucked in the suction stroke are performed. ,
Among the plurality of rotating members (31, 32, 91, 92), one rotating member (31, 91) has a rotational phase advanced than the other rotating members (32, 92).
When the working chamber (41, 81) formed by the one rotating member (31, 91) among the plurality of working chambers (41, 42, 81, 82) is an upstream working chamber,
The inner peripheral surface forming member (10, 60) may be connected to the upstream working chamber (41, 81) from the plurality of working chambers (41, 42, 81, 82) after completion of the suction stroke. Discharge passages (105a, 605a) reaching other working chambers (42, 82) that are compressing the fluid are formed. When the other working chamber (42, 82) is a downstream working chamber,
A mechanism (31, 32, 91, 92) for closing the discharge passage (105a, 605a) when the internal pressure of the upstream working chamber (41, 81) is lower than the internal pressure of the downstream working chamber (42, 82). The compressor according to claim 1, further comprising: The upstream working chamber (41, 81) and the downstream working chamber (42, 82) are arranged adjacent to each other in the axial direction of the upstream working chamber (41, 81),
The inner peripheral surface forming member (10, 60) has a plate-like partition (105, 605) that partitions the upstream working chamber (41, 81) and the downstream working chamber (42, 82). ,
The discharge passage (105a, 605a) is formed in the partition (105, 605),
The compressor according to claim 2, wherein a mechanism for closing the discharge passage (105a, 605a) is constituted by the rotating member (31, 32, 91, 92). The inner peripheral surface (101b, 102b) has a circular cross section,
The rotating members (31, 32) are disk-shaped rolling pistons that rotate eccentrically along the inner peripheral surfaces (101b, 102b),
The partition member (51, 52) is a vane that protrudes and intrudes from the inner peripheral surface (101b, 102b) and contacts the rolling piston (31, 32). The compressor according to one. The inner peripheral surface (101b, 102b) has a circular cross section,
The rotating members (31, 32) are disk-shaped rolling pistons that rotate eccentrically along the inner peripheral surfaces (101b, 102b),
The partition members (51, 52) are vanes that protrude from the inner peripheral surfaces (101b, 102b) and come into contact with the rolling pistons (31, 32),
The upstream working chamber (41) and the downstream working chamber (42) are arranged adjacent to each other in the axial direction of the upstream working chamber (41),
The inner peripheral surface forming member (10) has a plate-like partition (105) that partitions the upstream working chamber (41) and the downstream working chamber (42),
The discharge passage (105a) is formed in the partition (105),
The opening range with respect to the partition part (105) is different between the end part on the upstream working chamber (41) side and the end part on the downstream working chamber (42) side in the discharge passage (105a). The compressor according to claim 3.   The discharge passage (105a) includes a through-hole portion (105b) extending parallel to the thickness direction of the partition portion (105), and the upstream-side working chamber (41) of the through-hole portion (105b). 6. The compressor according to claim 5, wherein the compressor comprises a groove portion (105c) extending from an end portion along a plate surface of the partition portion (105). The inner peripheral surface (602b, 603b) has a circular cross section,
The rotating members (91, 92) are rotors that rotate in contact with the inner peripheral surfaces (602b, 603b),
The partition member (93, 94) is a vane that protrudes and protrudes from an outer peripheral surface of the rotor (91, 92) and contacts the inner peripheral surface (602b, 603b). The compressor as described in any one. The inner peripheral surface (602b, 603b) has a circular cross section,
The rotating members (91, 92) are rotors that rotate in contact with the inner peripheral surfaces (602b, 603b),
The partition members (93, 94) are vanes that protrude from the outer peripheral surface of the rotor (91, 92) and come into contact with the inner peripheral surfaces (602b, 603b),
The upstream working chamber (81) and the downstream working chamber (82) are arranged adjacent to each other in the axial direction of the upstream working chamber (81),
The inner peripheral surface forming member (60) has a plate-like partition (605) that partitions the upstream working chamber (81) and the downstream working chamber (82),
The discharge passage (605a) is formed in the partition (605),
An end of the discharge passage (605a) on the upstream working chamber (81) side overlaps with the rotor (91) forming the upstream working chamber (81),
An end of the discharge passage (605a) on the downstream working chamber (82) side overlaps with the rotor (92) forming the downstream working chamber (82),
The rotor (91) forming the upstream working chamber (81) is formed with an upstream communication passage (91b) for communicating the discharge passage (605a) with the upstream working chamber (81),
The rotor (92) forming the downstream working chamber (82) is formed with a downstream communication passage (92b) for communicating the discharge passage (605a) with the downstream working chamber (82). The compressor according to claim 3. The upstream communication path (91b) is constituted by a groove formed on an end surface of the rotor (91) forming the upstream working chamber (81) on the partition part (605) side,
The downstream communication path (92b) is configured by a groove formed on an end surface of the rotor (92) forming the downstream working chamber (82) on the partition part (605) side. The compressor according to claim 8. When the other working chamber (42, 82) is a downstream working chamber,
The maximum volume of the downstream working chamber (42, 82) is smaller than the maximum volume of the upstream working chamber (41, 81). The compressor described.   The rotating members (31, 32, 91, 92) forming a plurality of working chambers (41, 42, 81, 82) are configured so that the rotational phase difference between them is non-uniform. The compressor according to any one of claims 1 to 9, characterized in that:

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