JP5960412B2 - Multi-cylinder rotary compressor and refrigeration cycle apparatus - Google Patents

Description

  Embodiments described herein relate generally to a multi-cylinder rotary compressor and a refrigeration cycle apparatus using the multi-cylinder rotary compressor.

  In the refrigeration cycle apparatus, a multi-cylinder rotary compressor having a plurality of (mainly two) cylinders each having a cylinder chamber in a compression mechanism section is frequently used. In this type of multi-cylinder rotary compressor, it is advantageous if it is possible to switch between full-capacity operation in which gas refrigerant is compressed simultaneously in all cylinders and low-capacity operation in which some cylinders stop compression of gas refrigerant. It is.

  As a multi-cylinder rotary compressor having two cylinders and capable of switching between full-capacity operation and low-capacity operation as required, the one described in Patent Document 1 below is known.

  The multi-cylinder rotary compressor described in Patent Document 1 includes two cylinders, a roller provided to be eccentrically rotatable in the cylinder chamber of each cylinder, and a tip provided in each cylinder chamber with an outer peripheral surface of the roller. The cylinder chamber is provided with two high-pressure-side and low-pressure-side blades that are urged in the direction of contact with the roller, and the tip portion is in contact with the outer peripheral surface of the roller. The blade is slidably received in a blade groove formed in the cylinder, and a blade back chamber communicates with the blade groove.

  A spring member is accommodated in the blade back chamber of one cylinder, and the tip of the blade is always in contact with the outer peripheral surface of the roller by the urging force of the spring member. Thus, during operation of the multi-cylinder rotary compressor, compression is always performed in this cylinder.

  A high pressure gas refrigerant and a low pressure gas refrigerant are selectively supplied to the blade back chamber of the other cylinder. When a high-pressure gas refrigerant is supplied to the blade back chamber, the blade is urged by the pressure, the tip of the blade comes into contact with the outer peripheral surface of the roller, and compression is also performed in this cylinder. On the other hand, when a low-pressure gas refrigerant is supplied to the blade back chamber, the blade is not biased toward the roller, and the tip of the blade is separated from the outer peripheral surface of the roller, and the compression in this cylinder is stopped. It becomes the non-compression operation state.

  A blade back chamber formed in a cylinder that is switched between a state in which compression is performed (compression operation state) and a non-compression operation state in which compression is stopped (cylinderless state) includes a permanent magnet and a holding member that holds the permanent magnet. Is housed. This permanent magnet magnetically attracts the blade in a cylinder resting state in which compression is stopped by supplying a low-pressure gas refrigerant to the blade back chamber. When the blade is magnetically attracted to the permanent magnet in the idle cylinder state, the blade hits the permanent magnet holding member. However, in this case, since the blade gently hits the holding member, the holding member is not deformed even when the blade hits the holding member.

JP 2011-127475 A

  However, in the multi-cylinder rotary compressor described in Patent Document 1, when a liquid back phenomenon occurs in which liquid refrigerant enters the cylinder chamber during full-capacity operation, the pressure in the cylinder chamber suddenly rises and the blade becomes a blade back chamber. The rear end of the blade may violently collide with the permanent magnet holding member.

  An object of an embodiment of the present invention is to use a multi-cylinder rotary compressor capable of preventing a blade from colliding with a permanent magnet holding member when a liquid back phenomenon occurs, and the multi-cylinder rotary compressor. A refrigeration cycle apparatus is provided.

In the multi-cylinder rotary compressor according to the embodiment, an electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft are accommodated in a sealed case. The compression mechanism part includes a first cylinder chamber. And a first cylinder that can be switched between a compression operation state and a non-compression operation state that is a non-compression operation state, and a second cylinder that has a second cylinder chamber and is always in a compression operation state. In a multi-cylinder rotary compressor that discharges working fluid compressed by a cylinder and a second cylinder into a sealed case, a first roller that is provided in a first cylinder chamber and is connected to a rotating shaft and rotates eccentrically, A slidable first blade provided in one cylinder chamber, the tip of which contacts the outer peripheral surface of the first roller and divides the first cylinder chamber into a high pressure side and a low pressure side; Formed and slidable with first blade A first blade groove accommodated in the first cylinder, a first blade back chamber formed in the first cylinder and communicated with the first blade groove, and communicated with the first blade back chamber. A back pressure introduction passage for supplying the working fluid and a permanent magnet that is accommodated in the first blade back chamber and is magnetically attracted by moving the first blade away from the first roller when the first cylinder is in a cylinder deactivation state. The holding member and the first cylinder are formed so as to protrude toward the first blade . When the first blade moves to the holding member side, it collides with the first blade and prevents the first blade from colliding with the holding member. A collision preventing means including a protruding portion .

It is sectional drawing of the multicylinder rotary compressor of 1st Embodiment, and the block diagram of the refrigerating-cycle apparatus containing this multicylinder rotary compressor. It is a disassembled perspective view which shows a part of compression mechanism part. It is a longitudinal cross-sectional view which expands and shows a part of compression mechanism part. It is a longitudinal cross-sectional view which expands and shows a part of compression mechanism part when a liquid back phenomenon generate | occur | produces. When the liquid back phenomenon occurs, it is an explanatory view further enlarging a state where the rear end portion of the first blade collides with the protrusion and does not collide with the holding member. It is a figure which expands and shows the closing member attached to a 1st cylinder, the valve pressing member attached to the closing member, and a valve body. FIG. 7 is a sectional view taken along line XX in FIG. 6. It is sectional drawing of the state which piled up two obstruction | occlusion members with which the valve pressing member and the valve body were attached. It is a front view which shows the 1st braid | blade of 2nd Embodiment. It is a longitudinal cross-sectional view which expands and shows a part of compression mechanism part when the liquid back phenomenon in 2nd Embodiment generate | occur | produces. It is a front view which shows the 1st braid | blade of 3rd Embodiment. It is a longitudinal cross-sectional view which expands and shows a part of compression mechanism part when the liquid back phenomenon in 3rd Embodiment generate | occur | produces.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
1st Embodiment is described based on FIG. 1 thru | or FIG. FIG. 1 is a schematic cross-sectional view of a multi-cylinder rotary compressor A and a configuration diagram of a refrigeration cycle apparatus B including the multi-cylinder rotary compressor A.

  First, the multi-cylinder rotary compressor A will be described. The multi-cylinder rotary compressor A is a device that compresses a gas refrigerant that is a working fluid. The multi-cylinder rotary compressor A has a cylindrical sealed case 1, and a compression mechanism 2 is accommodated in a lower portion of the sealed case 1. The electric motor unit 3 is accommodated in the upper part. The compression mechanism unit 2 and the electric motor unit 3 are connected via a rotating shaft 4 extending in the vertical direction, and the compression mechanism unit 2 is driven by a driving force generated in the electric motor unit 3.

  The compression mechanism part 2 has the 1st cylinder 5a located in the lower part side, and the 2nd cylinder 5b located in the upper part side. A sub bearing 6 is attached to the lower end surface of the first cylinder 5a, and a main bearing 7 is attached to the upper end surface of the second cylinder 5b. A partition plate 8 is interposed between the first cylinder 5a and the second cylinder 5b.

  The rotary shaft 4 is pivotally supported by the main bearing 7 and the auxiliary bearing 6 and is provided so as to penetrate through the first and second cylinders 5a and 5b. A first eccentric part 9a located in the first cylinder 5a and a second eccentric part 9b located in the second cylinder 5b are formed on the rotating shaft 4 with a phase difference of 180 °. The first eccentric portion 9a and the second eccentric portion 9b are formed to have the same diameter, the first eccentric portion 9a is fitted with a cylindrical first roller 10a, and the second eccentric portion 9b has a cylindrical second shape. The roller 10b is fitted.

  A first cylinder chamber 11a is formed inside the first cylinder 5a. The first cylinder chamber 11a is a space in which both ends in the vertical direction are covered with the partition plate 8 and the auxiliary bearing 6 to compress the gas refrigerant. Inside the second cylinder 5b, a second cylinder chamber 11b is formed in which both ends in the vertical direction are covered with the main bearing 7 and the partition plate 8 and serve as a space for compressing the gas refrigerant.

  The first cylinder chamber 11a and the second cylinder chamber 11b are formed with the same inner diameter and the same height. The first and second rollers 10a and 10b are rotated eccentrically while part of the peripheral walls of the first and second rollers 10a and 10b are in line contact with the peripheral walls of the first and second cylinder chambers 11a and 11b, respectively. 10a and 10b are accommodated in the first and second cylinder chambers 11a and 11b.

  Double discharge mufflers 12 are attached to the main bearing 7 to cover the discharge valve mechanism 13 provided on the main bearing 7. The discharge muffler 12 is formed with a discharge hole (not shown) communicating with the inside of the sealed case 1. A single discharge muffler 14 is attached to the auxiliary bearing 6 and covers a discharge valve mechanism (not shown) provided in the auxiliary bearing 6.

  The discharge valve mechanism 13 provided in the main bearing 7 is provided opposite to the second cylinder chamber 11b, and opens when the pressure in the second cylinder chamber 11b becomes equal to or higher than a predetermined value due to the compression action. The high-pressure gas refrigerant compressed in the second cylinder chamber 11 b is discharged into the discharge muffler 12. The gas refrigerant discharged into the discharge muffler 12 is discharged into the sealed case 1 through a discharge hole formed in the discharge muffler 12. The discharge valve mechanism provided in the sub-bearing 6 is provided opposite to the first cylinder chamber 11a and opens when the pressure in the first cylinder chamber 11a exceeds a predetermined value, and the first cylinder chamber The high-pressure gas refrigerant compressed in 11 a is discharged into the discharge muffler 14.

  A discharge gas guide path (leading high pressure gas refrigerant discharged into the discharge muffler 14) into the discharge muffler 12 across the auxiliary bearing 6, the first cylinder 5a, the partition plate 8, the second cylinder 5b and the main bearing 7. (Not shown) is formed. As a result, the gas refrigerant discharged from the first cylinder chamber 11a into the discharge muffler 14 is guided into the discharge muffler 12 through the discharge gas guide path and together with the gas refrigerant compressed in the second cylinder chamber 11b. It is discharged into the sealed case 1.

  An oil reservoir 15 in which lubricating oil is stored is formed at the bottom of the sealed case 1. In FIG. 1, a solid line across the flange portion of the main bearing 7 indicates the oil level of the lubricating oil stored in the oil reservoir 15. Almost all of the compression mechanism 2 is immersed in the lubricating oil stored in the oil reservoir 15.

  FIG. 2 is an exploded perspective view showing a part of the compression mechanism section 2. A first blade groove 16a having one end communicating with the first cylinder chamber 11a and a first blade back chamber 17a communicating with the other end of the first blade groove 16a are formed in the first cylinder 5a. The first blade 18a is slidably accommodated in the first blade groove 16a.

  A counterbore part 19 is formed in the back part of the first blade back chamber 17a along the sliding direction of the first blade 18a, and a permanent magnet 20 and a holding member that holds the permanent magnet 20 in the counterbore part 19 are formed. 21 is accommodated. The permanent magnet 20 magnetically attracts the first blade 18a in a cylinder resting state, which is a non-compression operation state in which the compression of the gas refrigerant in the first cylinder 5a is stopped. Above the spot facing 19, a protrusion 27 is formed as a collision preventing means.

  A second blade groove 16b having one end communicating with the second cylinder chamber 11b and a second blade back chamber 17b communicating with the other end of the second blade groove 16b are formed in the second cylinder 5b. A second blade 18b is slidably accommodated in the second blade groove 16b.

  The first and second blades 18a and 18b are formed so that the tip portions of the first and second blades 18a and 18b have a substantially arc shape, and the tip portions of the first and second blades 18a and 18b appear and disappear in the first and second cylinder chambers 11a and 11b. Further, the first and second blades 18a and 18b are formed to have dimensions such that the rear end portions thereof protrude and appear in the opposed first and second blade back chambers 17a and 17b.

  First and second rollers 10a, 18b projecting into the first and second cylinder chambers 11a, 11b and accommodated in the first and second cylinder chambers 11a, 11b, When abutting against the outer peripheral surface of 10b, the first and second blades 18a and 18b are in line contact regardless of the rotation angles of the first and second rollers 10a and 10b. The first and second cylinder chambers 11a and 11b are divided into two parts by the tips of the first and second blades 18a and 18b coming into contact with the outer peripheral surfaces of the first and second rollers 10a and 10b. As the first and second rollers 10a and 10b rotate eccentrically, one section becomes the high pressure side and the other section becomes the low pressure side.

  The second cylinder 5b is formed with a lateral hole 22 that communicates the second blade back chamber 17b and the outer peripheral surface of the second cylinder 5b, and a spring member 23 that is an elastic body is accommodated in the lateral hole 22. ing. When the second cylinder 5b that accommodates the spring member 23 in the horizontal hole 22 and accommodates the second blade 18b in the second blade groove 16b is accommodated in the sealed case 1, the spring member 23 is contained in the sealed case 1. It is interposed between the peripheral surface and the rear end portion of the second blade 18b, and applies back pressure to the second blade 18b. The second blade 18b, to which the back pressure is applied by the spring member 23, is maintained in a state in which the tip thereof is in contact with the outer peripheral surface of the second roller 10b.

  On the other hand, in the first cylinder 5a, when a high-pressure gas refrigerant is supplied to the first blade back chamber 17a, the tip of the first blade 18a is brought into contact with the outer peripheral surface of the first roller 10a, and the first cylinder 5a A compression operation state is entered. In addition, when a low-pressure gas refrigerant is supplied to the first blade back chamber 17b, the tip of the first blade 18a is separated from the outer peripheral surface of the first roller 10a, and the first cylinder 5a is in a cylinder resting state.

  Returning to FIG. The first blade back chamber 17a of the first cylinder 5a is formed at a position projecting outward from the peripheral edge of the flange portion of the sub-bearing 6, and the upper and lower surfaces are opened as it is and opened into the sealed case 1.

  However, the upper surface opening of the first blade back chamber 17 a is covered with the partition plate 8. Further, a closing member 24 is attached to the lower side of the first cylinder 5a, and the lower surface opening of the first blade back chamber 17a is covered with the closing member 24. Therefore, the first blade back chamber 17a has a sealed structure in which the upper and lower surface openings are closed by the partition plate 8 and the closing member 24.

  The side end surface of the closing member 24 on the auxiliary bearing 6 side is formed in a shape along the peripheral end surface of the flange portion of the auxiliary bearing 6, and the side end surface opposite to the side end surface has a high pressure relative to the first blade back chamber 17 a. Alternatively, one end side of the back pressure introduction passage 25 for supplying a low-pressure gas refrigerant is connected. Further, a check valve mechanism 26 is provided on the closing member 24. When a high-pressure gas refrigerant is supplied to the first blade back chamber 17a, the tip of the first blade 18a is in contact with the outer peripheral surface of the first roller 10a.

  Based on FIG. 3 thru | or FIG. 5, the positional relationship of the member arrange | positioned in the 1st cylinder 5a of the compression mechanism part 2 and its periphery is demonstrated. The first blade back chamber 17a communicated with the cylinder chamber 11a has a height dimension of “H”, and the counterbore portion 19 has a height dimension of “h (h <H)”. The upper part of the counterbore part 19 formed in the back part of the first blade back chamber 17a has a height dimension that is a difference between these height dimensions "H" and "h", and the first blade groove A protrusion 27 is formed as a collision preventing means that protrudes toward the first blade 18a accommodated in 16a. The height dimension of the permanent magnet 20 accommodated in the spot facing portion 19 and the holding member 21 is the same as or smaller than “h”. Further, the width dimension “l” along the sliding direction of the first blade 18 a between the permanent magnet 20 and the holding member 21 accommodated in the spot facing portion 19 is the depth dimension of the spot facing portion 19 (the protrusion of the projection 27. The height is smaller than “L”.

  4 and 5 show a state in which a liquid back phenomenon in which the liquid refrigerant enters the first cylinder chamber 11a occurs, and the first blade 18a jumps out toward the first blade back chamber 17a. In this case, the width dimension “l” of the permanent magnet 20 and the holding member 21 along the sliding direction of the first blade 18 a is smaller than the depth dimension of the spot facing 19 (projection height of the protrusion 27) “L”. Therefore, the first blade 18a jumping out toward the first blade back chamber 17a stops at the position where the rear end portion collides with the protrusion 27, and the rear end portion of the first blade 18a collides with the holding member 21. Is prevented. 3 and 4, 10 a is a first roller, 16 a is a first blade groove, 6 is a secondary bearing, and 24 is a closing member 24.

  FIG. 6 shows an enlarged view of the attachment state of the closing member 24 and the check valve mechanism 26 to the closing member 24. The closing member 24 is fixed to a first cylinder (not shown) by a mounting bolt 28, and a valve pressing member 29 and a valve body 30 constituting the check valve mechanism 26 are mounted by a mounting bolt 31 which is a mounting member. Yes.

  7 is a cross-sectional view taken along line XX in FIG. When the closing member 24 is attached to the first cylinder 5a, the closing member 24 is supplied through a recess 32 located on the side facing the first cylinder 5a and the back pressure introduction passage 25 (see FIG. 1). A hole 33 that guides the high-pressure or low-pressure gas refrigerant into the recess 32 and a communication path 34 that communicates the recess 32 with the inside of the sealed case are formed. A check valve mechanism 26 having a valve pressing member 29 and a valve body 30 is attached to a side of the closing member 24 opposite to the side facing the first cylinder 5 a by a mounting bolt 31. The valve body 30 opens and closes the communication path 34 according to the pressure difference between the pressure in the first blade back chamber 17a and the pressure in the sealed case 1. That is, in the compression operation state in which the high-pressure gas refrigerant is guided from the back pressure introduction passage 25 (see FIG. 1) through the hole 33 into the first blade back chamber 17a, the first blade 18a is connected to the first cylinder chamber 11a. When the pressure in the first blade back chamber 17a becomes larger than the pressure in the sealed case 1, the valve body 30 opens the communication path 34. . Therefore, it is possible to prevent the pressure in the first blade back chamber 17a from becoming excessive. In particular, a great effect can be obtained when liquid fluid such as lubricating oil or liquid refrigerant exists in the first blade back chamber 17a and the back pressure introduction passage 25. Further, when the first blade 18a slides (advances) from the first blade back chamber 17a side to the first cylinder chamber 11a side, and the pressure in the first blade back chamber 17a becomes equal to or lower than the pressure in the sealed case 1 Or, when a low-pressure gas refrigerant is introduced into the first blade back chamber 17a, the valve body 30 closes the communication passage 34. The valve pressing member 29 restricts the maximum opening of the valve body 30.

  FIG. 8 shows a state in which the two closing members 24 to which the valve body 30 and the valve pressing member 29 are attached with the attachment bolts 31 are overlapped in the same direction with the concave portion 32 facing downward. The recess 32 is formed in a size that can accommodate the valve body 30, the valve pressing member 29, and the mounting bolt 31, and when the two closing members 24 are stacked, the valve body 30 and the valve pressing member 29 of one closing member 24 are stacked. And the mounting bolt 31 are accommodated in the recess 32 of the other closing member 24.

  Returning again to FIG. A discharge pipe 35 through which high-pressure gas refrigerant in the sealed case 1 is discharged out of the sealed case 1 is connected to an upper end portion of the sealed case 1 constituting the multi-cylinder rotary compressor A. The discharge pipe 35 is connected to the upper end of an accumulator 39 via a condenser 36, an expansion device 37 and an evaporator 38. The accumulator 39 and the multi-cylinder rotary compressor A are connected via a suction pipe 40.

  The refrigeration cycle apparatus B is configured by sequentially connecting the multi-cylinder rotary compressor A, the condenser 36, the expansion device 37, the evaporator 38, and the accumulator 39 as described above.

  The suction pipe 40 penetrates the sealed case 1 and is connected to the peripheral end surface of the partition plate 8. In the partition plate 8, a suction guide path (not shown) is provided in the axial direction from the peripheral surface portion to which the suction pipe 40 is connected. The tip of the suction guide path is bifurcated into a diagonally upward and diagonally downward direction. The branch guideway branched obliquely downward is communicated with the first cylinder chamber 11a, and the branch guideway branched obliquely upward is communicated with the second cylinder chamber 11b. Therefore, the accumulator 39 and the first and second cylinder chambers 11a and 11b of the multi-cylinder rotary compressor A are always in communication.

  The other end side of the back pressure introduction passage 25 extends to a position above the upper ends of the sealed case 1 and the accumulator 39, and a pressure switching valve 41 is provided at the tip thereof. The pressure switching valve 41 uses a four-way switching valve used in an air conditioner equipped with a heat pump refrigeration cycle capable of switching between cooling and heating operations, thereby reducing costs.

  A first branch pipe (high pressure pipe) 42 is branched from the discharge pipe 35 connected to the upper end of the sealed case 1, and the first branch pipe 42 is connected to the first port Pa of the pressure switching valve 41. . The pressure switching valve 41 has three ports (second port Pb, third port Pc, and fourth port Pd) in addition to the first port Pa, and the back pressure introduction passage 25 is connected to the second port Pb. ing. The third port Pc is connected to a second branch pipe (low pressure pipe) 43a that branches from a pipe 43 through which the low-pressure gas refrigerant flows through the evaporator 38 and the accumulator 39. The fourth port Pd is always closed by the plug body 44.

  An inverted U-shaped valve body 45 is movably provided inside the pressure switching valve 41. The inverted U-shaped valve body 45 communicates the position where the third port Pc and the fourth port Pd communicate with each other as indicated by a solid line, and the second port Pb and the third port Pc as indicated by a broken line. It is possible to switch electromagnetically to the position to be performed. The first port Pa is always open.

  Further, when the inverted U-shaped valve body 45 is located at the position indicated by the solid line, the first port Pa and the second port Pb are communicated, and the third port Pc and the fourth port Pd are connected. It communicates via an inverted U-shaped valve body 45. However, since the fourth port Pd is always closed by the plug body 44, only the communication between the first port Pa and the second port Pb remains as the communication state in the pressure switching valve 41.

  When the inverted U-shaped valve body 45 moves to the position indicated by the broken line, the second port Pb and the third port Pc are communicated with each other via the inverted U-shaped valve body 45, and the first port Pa and the fourth port The port Pd is communicated. However, since the fourth port Pd is always closed by the plug body 44, only the communication between the second port Pb and the third port Pc remains as the communication state in the pressure switching valve 41.

  As the pressure switching valve 41, a case where a four-way switching valve which is a standard product used in a refrigeration cycle constituting a normal heat pump air conditioner is used as an example has been described. Similar effects can be obtained by using a valve or combining a plurality of on-off valves.

  In such a configuration, in the multi-cylinder rotary compressor A, the high-pressure gas refrigerant compressed by the compression mechanism unit 2 is discharged into the sealed case 1, and the high-pressure gas refrigerant in the sealed case 1 is discharged into the discharge pipe 35. Is led to the condenser 36 side, and a refrigeration cycle is performed.

  Further, the multi-cylinder rotary compressor A stops the full-capacity operation in which the gas refrigerant is compressed in both the first cylinder 5a and the second cylinder 5b and the compression in the first cylinder 5a to stop the second cylinder 5b. The full capacity operation and the low capacity half operation can be described. Switching between full capacity operation and low capacity half operation is performed by switching the position of the inverted U-shaped valve body 45 of the pressure switching valve 41.

  First, during full capacity operation, the inverted U-shaped valve body 45 is moved to the position indicated by the solid line in FIG. By moving the inverted U-shaped valve body 45 to the position indicated by the solid line, the first port Pa and the second port Pb are communicated with each other. Thereby, a part of the high-pressure gas refrigerant discharged from the sealed case 1 to the discharge pipe 35 is guided to the pressure switching valve 41 through the first branch pipe 42, and the high-pressure gas refrigerant is supplied to the back pressure introduction passage 25. And supplied to the first blade back chamber 17a.

  By supplying a high-pressure gas refrigerant to the first blade back chamber 17a, this pressure acts as a back pressure on the rear end portion of the first blade 18a, and this back pressure is supplied into the first cylinder chamber 11a. Since it is higher than the pressure of the gas refrigerant, the tip of the first blade 18a is brought into contact with the outer peripheral surface of the first roller 10a, and the inside of the first cylinder chamber 11a is divided into two by the first blade 18a.

  When the low-pressure gas refrigerant is supplied into the first cylinder chamber 11a through the suction pipe 40, the low-pressure gas refrigerant supplied into the first cylinder chamber 11a is compressed by the eccentric rotation of the first roller 10a. The compressed and high-pressure gas refrigerant is discharged into the discharge muffler 14, and the gas refrigerant discharged into the discharge muffler 14 is discharged into the sealed case 1 via the discharge muffler 12.

  On the other hand, in the second cylinder 5b, one end side of the spring member 23 is in contact with the rear end portion of the first blade 18b. Then, the urging force of the spring member 23 acts on the first blade 18b, the tip of the second blade 18b comes into contact with the outer peripheral surface of the second roller 10b, and the second cylinder chamber 11b is moved by the second blade 18b. It is divided into two.

  When a low-pressure gas refrigerant is supplied into the second cylinder chamber 11b through the suction pipe 40, the low-pressure gas refrigerant supplied into the second cylinder chamber 11b is compressed by the eccentric rotation of the second roller 10b. The compressed and high-pressure gas refrigerant is discharged into the discharge muffler 12 and further discharged into the sealed case 1 from the discharge muffler 12.

  As described above, during full capacity operation, the first cylinder 5a and the second cylinder 5b are both in the compression operation state, and the gas refrigerant is compressed.

  Next, at the time of the low-performance operation, the inverted U-shaped valve body 45 is moved to the position indicated by the broken line in FIG. When the inverted U-shaped valve body 45 moves to the position indicated by the broken line, the second port Pb and the third port Pc are communicated. As a result, the second branch pipe 43 a and the back pressure introduction passage 25 are communicated, and a part of the low-pressure gas refrigerant flowing in the pipe 43 passes through the second branch pipe 43 a and the back pressure introduction passage 25 to the first. It is supplied to the blade back chamber 17a.

  When a low-pressure gas refrigerant is supplied to the first blade back chamber 17a, this pressure is the same as the pressure of the gas refrigerant supplied into the first cylinder chamber 11a, so that the first blade 18a has the first roller 10a. The tip of the first blade 18a is not in contact with the outer peripheral surface of the first roller 10a. For this reason, the inside of the 1st cylinder chamber 11a is not divided into two, and even if the 1st roller 10a rotates eccentrically in the 1st cylinder chamber 11a, compression of a gas refrigerant is not performed.

  On the other hand, in the second cylinder chamber 11b, the tip of the first blade 18b is brought into contact with the outer peripheral surface of the second roller 10b by the urging force of the spring member 23, and the gas refrigerant is compressed.

  As described above, during the low capacity half operation, the second cylinder 5b is in the compression operation state and the gas refrigerant is compressed, and the first cylinder 5a is in the cylinder resting state and the compression of the gas refrigerant is stopped.

  When the first cylinder 5a is in a cylinder resting state, the first blade 18a is magnetically attracted to the permanent magnet 20 accommodated in the blade back chamber 17a.

  When a liquid back phenomenon occurs in which liquid refrigerant enters the first and second cylinder chambers 11a and 11b during full capacity operation in which gas refrigerant is compressed in the first and second cylinders 5a and 5a, the first The pressure in the second cylinder chambers 11a and 11b rises rapidly, and the first and second blades 18a and 18b jump out toward the first and second blade back chambers 17a and 17b.

  4 and 5 show a state in which a liquid back phenomenon in which the liquid refrigerant enters the first cylinder chamber 11a occurs, and the first blade 18a jumps out toward the first blade back chamber 17a. In this case, since the width dimension “l” of the permanent magnet 20 and the holding member 21 along the sliding direction of the first blade 18 a is smaller than the depth dimension “L” of the spot facing portion 19, the first blade back chamber 17 a side The first blade 18a that has bounced off is stopped at the position where its rear end collides with the protrusion 27, and the rear end of the first blade 18a is prevented from colliding with the holding member 21. Thereby, it is possible to prevent the rear end portion of the first blade 18a from colliding with the holding member 21 and deforming the holding member 21, and further, the deformation proceeds and the sliding operation of the first blade 18a is performed. Can be prevented from occurring.

  FIG. 8 shows a state in which the two closing members 24 each having the valve body 30 and the valve pressing member 29 attached by the attachment bolts 31 are overlapped in the same direction and the concave portion 32 is directed downward. When the valve body 30, the valve pressing member 29, and the mounting bolt 31 are opposed to the recess 32 and the two closing members 24 are overlapped, the valve body 30, the valve pressing member 29 and the mounting bolt 31 are accommodated in the recess 32. The For this reason, when storing or transporting the valve body 30 and the valve pressing member 29 attached to the closing member 24, the storage space can be reduced, and the cargo to be transported can be downsized. . Further, since the closing member 24 is conveyed to the assembly site of the multi-cylinder rotary compressor A with the valve body 30 and the valve presser member 29 attached, the number of steps when the multi-cylinder rotary compressor A is assembled is increased. The assembly work of the multi-cylinder rotary compressor A can be facilitated.

  In the present embodiment, the case where the protrusion 27 is formed on the first cylinder 5a as an example of collision prevention has been described as an example. However, instead of the protrusion 27, the first cylinder 5a collides with a separate body. A prevention means may be provided, and the collision prevention means may be fixed at a position where the protrusion 27 is formed.

(Second Embodiment)
A second embodiment will be described with reference to FIGS. 9 and 10. Note that, in the second embodiment and other embodiments, the same components as those described in the first embodiment are denoted by the same reference numerals, and redundant descriptions are omitted.

  The basic structure of the second embodiment is the same as that of the first embodiment. The difference of the second embodiment from the first embodiment is the structure of the collision preventing means and the permanent attachment to the blade back chamber 17a. This is a housing structure for the magnet 20 and the holding member 21.

  FIG. 9 is a front view showing the first blade 18aa of the second embodiment, and a protrusion 46, which is a collision preventing means, is formed on one end side of the first blade 18aa. The height of the protrusion 46 is “Hb”.

  FIG. 10 shows a liquid back phenomenon in which liquid refrigerant enters the first cylinder chamber 11a in which the first blade 18aa is accommodated, and the first blade 18aa slidably accommodated in the first blade groove 16a is the first blade. The state which protruded to the back chamber 17a side is shown.

  When the first blade 18aa is accommodated in the first blade groove 16a, the protrusion 46 formed on the first blade 18aa protrudes in a direction facing the first blade back chamber 17a.

  A permanent magnet 20 and a holding member 21 that holds the permanent magnet 20 are accommodated in the back of the first blade back chamber 17a. The height dimension of the first blade back chamber 17a is “H”, the height dimension of the permanent magnet 20 and the holding member 21 is “Ha”, and “Ha” is smaller than “H”.

  The height dimension of the protrusion 46 formed on the first blade 18aa is “Hb”. This “Hb” is the height dimension “H” of the blade back chamber 17a and the height of the permanent magnet 20 and the holding member 21. It is formed smaller than the difference dimension from the height dimension “Ha”.

  Further, the dimension “La” from the rear end portion of the first blade 18aa other than the protrusion 46 to the tip of the protrusion 46 is determined by the relationship between the permanent magnet 20 and the holding member 21 along the sliding direction of the first blade 18aa. It is formed larger than the width dimension “l”.

  In such a configuration, the dimension “La” from the rear end portion of the first blade 18aa other than the projection 46 to the tip of the projection 46 is held with the permanent magnet 20 along the sliding direction of the first blade 18aa. It is formed larger than the width dimension “l” with the member 21. Further, the height dimension “Hb” of the protrusion 46 is formed smaller than the difference between the height dimension “H” of the first blade back chamber 17 a and the height dimension “Ha” of the permanent magnet 20 and the holding member 21. ing.

  For this reason, when the liquid back phenomenon occurs and the first blade 18aa jumps to the first blade back chamber 17a side, as shown in FIG. 10, the protrusion 46 is formed on the peripheral wall of the first blade back chamber 17a. Thus, it collides with the upper region of the permanent magnet 20 and the holding member 21, and the rear end portion of the first blade 18aa is prevented from colliding with the holding member 21. As a result, the rear end portion of the first blade 18aa can be prevented from colliding with the holding member 21 and the holding member 21 can be prevented from being deformed, and further, the deformation proceeds and the first blade 18aa slides. Can be prevented from occurring.

(Third embodiment)
A third embodiment will be described with reference to FIGS. 11 and 12. The basic structure of the third embodiment is the same as that of the first embodiment, and the difference between the third embodiment and the first embodiment is the shape of the rear end portion of the first blade 18ab.

  FIG. 11 is a front view showing the first blade 18ab of the third embodiment, and an end C of the first blade 18ab is formed in a flat shape. This end C is the side facing the first blade back chamber 17a when the first blade 18ab is accommodated in the first blade groove 16a.

  FIG. 12 shows a liquid back phenomenon in which the liquid refrigerant enters the first cylinder chamber 11a in which the first blade 18ab is accommodated, and the first blade 18ab slidably accommodated in the blade groove 16a becomes the first blade back chamber. The state which bounced to the 17a side is shown.

  In the third embodiment, similarly to the first embodiment, a spot facing 19 is formed in the first cylinder 5a, and the permanent magnet 20 and the holding member 21 are accommodated in the spot facing 19. . A protrusion 27 is formed above the spot facing 19 in the first cylinder 5a. Further, the width dimension “l” between the permanent magnet 20 and the holding member 21 is formed to be smaller than the depth dimension “L” of the spot facing portion 19.

  In such a configuration, when the liquid back phenomenon occurs and the first blade 18ab jumps to the first blade back chamber 17a side, as shown in FIG. The end of the first blade 18ab stops at a position where it collides with the protrusion 27, and the rear end of the first blade 18ab is prevented from colliding with the holding member 21. As a result, it is possible to prevent the rear end portion of the first blade 18ab from colliding with the holding member 21 and deforming the holding member 21, and further, the deformation progresses to slide the first blade 18ab. Can be prevented from occurring.

  Further, since the rear end portion of the first blade 18ab is formed in a flat shape, the average distance between the rear end portion of the first blade 18ab and the permanent magnet 20 is reduced. Therefore, when the first blade 18ab is magnetically attracted by the permanent magnet 20 during the operation with a reduced capacity, the magnetic attraction performance can be improved.

  As mentioned above, although some embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1 ... Sealing case, 2 ... Compression mechanism part, 3 ... Electric motor part, 4 ... Rotary shaft, 5a ... 1st cylinder, 5b ... 2nd cylinder, 10a ... 1st roller, 11a ... 1st cylinder chamber, 11b ... 2nd Cylinder chamber, 16a ... first blade groove, 17a ... first blade back chamber, 18a ... first blade, 18aa ... first blade, 18ab ... first blade, 20 ... permanent magnet, 21 ... holding member, 14 ... closing member , 25 ... back pressure introduction passage, 27 ... projection (collision prevention means), 29 ... valve restraining member, 30 ... valve body, 31 ... mounting member, 32 ... recess, 34 ... communication passage, 36 ... condenser, 37 ... Expansion device 38 ... Evaporator 46 ... Projection (collision prevention means) A ... Multi-cylinder rotary compressor B ... Refrigeration cycle device

Claims (4)

An electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft are accommodated in the sealed case, and the compression mechanism part has a first cylinder chamber and is in a compressed operation state and an uncompressed operation. A first cylinder that can be switched to a cylinder resting state, and a second cylinder that has a second cylinder chamber and is always in a compression operation state, and is compressed by the first cylinder and the second cylinder. In the multi-cylinder rotary compressor that discharges the generated working fluid into the sealed case,
A first roller provided in the first cylinder chamber and connected to the rotating shaft to rotate eccentrically;
A slidable first blade provided in the first cylinder chamber, the tip portion of which is in contact with the outer peripheral surface of the first roller, and the first cylinder chamber is divided into a high pressure side and a low pressure side;
A first blade groove formed in the first cylinder and slidably receiving the first blade;
A first blade back chamber formed in the first cylinder and communicated with the first blade groove;
A back pressure introduction passage that communicates with the first blade back chamber and supplies the working fluid of high pressure or low pressure to the first blade back chamber;
A holding member that is housed in the first blade back chamber and holds a permanent magnet that magnetically attracts the first blade away from the first roller when the first cylinder is in a cylinder resting state;
The first cylinder is formed so as to protrude toward the first blade, and when the first blade moves toward the holding member, it collides with the first blade, and the first blade collides with the holding member. Anti-collision means comprising protrusions to prevent this,
A multi-cylinder rotary compressor. 2. The first blade has an end facing the first blade back chamber formed in a flat shape when the first blade is received in the first blade groove. The described multi-cylinder rotary compressor. A closing member that closes one side of the first blade back chamber and is connected to the back pressure introduction passage is attached to one side of the first cylinder,
The closure member is formed with a recess located on the side facing the first cylinder when the closure member is attached to the first cylinder, and a communication path communicating with the recess and the inside of the sealed case.
A valve body that opens and closes the communication path according to a pressure difference between the pressure in the first blade back chamber and the pressure in the sealed case on the opposite side of the closing member to the side facing the first cylinder, A valve pressing member that regulates the opening of the valve body, and an attachment member that attaches these valve body and the valve pressing member to the closing member;
The said valve body, the said valve pressing member, and the said attachment member are accommodated in the said recessed part when the two said obstruction | occlusion members are piled up in the same direction, The said recessed part is characterized by the above-mentioned. Multi-cylinder rotary compressor. The multi-cylinder rotary compressor according to any one of claims 1 to 3, a condenser connected to the multi-cylinder rotary compressor, an expansion device connected to the condenser, and the expansion device And an evaporator connected between the multi-cylinder rotary compressor.

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