Patent Grant
12060884
In recent years, a three-cylinder rotary compressor having three sets of refrigerant compression units arranged in the axial direction of a rotating shaft has been developed in order to increase the refrigerant compression capacity. Three sets of refrigerant compression units are interposed between a pair of bearings that support the rotating shaft, and a partition plate is provided between the refrigerant compression units adjacent to each other in the axial direction of the rotating shaft.
Furthermore, each of three sets of refrigerant compression units includes a cylinder chamber through which the rotating shaft penetrates. The cylinder chamber is partitioned in the axial direction of the rotating shaft by the partition plate and the end plates of the pair of bearings, and rollers are accommodated in each cylinder chamber. The roller eccentrically rotates in the cylinder chamber, integrally with the rotating shaft, to compress the refrigerant sucked into the cylinder chamber.
The refrigerant compressed in the cylinder chamber is discharged to the outside of the refrigerant compression unit through each discharge port. However, according to the conventional three-cylinder rotary compressor, particularly, securing the capacity of the discharge passage communicating with the cylinder chamber located in the middle is difficult since only one discharge port is present for each cylinder chamber.
As a result, the discharge loss and discharge pressure pulsation of the refrigerant discharged from the intermediate cylinder chamber cannot be sufficiently reduced, and room for improvement of the performance of the rotary compressor or improvement for noise suppression during operation of the rotary compressor is left.
Embodiments described herein aim to obtain a rotary compressor capable of suppressing the discharge loss and discharge pulsation of the working fluid discharged from all the cylinder chambers to a low level.
In general, according to one embodiment, the rotary compressor comprises a sealed container, a compression mechanism unit that compresses a working fluid inside the sealed container, and a drive source that is accommodated in the sealed container and drives the compression mechanism unit.
The compression mechanism unit includes a rotating shaft connected to the drive source inside the sealed container, a first bearing and a second bearing rotatably supporting the rotating shaft and including end plates extending in a radial direction of the rotating shaft, a first muffler chamber attached to the first bearing, a second muffler chamber attached to the second bearing, at least three cylinder bodies interposed between the first bearing and the second bearing, and spaced apart and arranged in an axial direction of the rotating shaft, each defining a cylinder chamber, a plurality of partition plates provided between the adjacent cylinder bodies, and a plurality of rollers fitted in the rotating shaft to compress the working fluid in the cylinder chambers, and the cylinder chambers of the at least three cylinder bodies are partitioned in an axial direction of the rotating shaft by the end plate of the first bearing, the end plate of the second bearing, and the partition plates.
Each of the end plate of the first bearing and the end plate of the second bearing includes a first discharge port discharging the working fluid compressed in the cylinder chamber of the cylinder body adjacent to the end plate to the first muffler chamber and the second muffler chamber, and each of the plurality of partition plates that sandwich the intermediate cylinder body located between the two cylinder bodies adjacent to the end plates includes an intermediate muffler chamber in which the working fluid flows, and a second discharge port discharging the working fluid compressed in the cylinder chamber of the intermediate cylinder body to the intermediate muffler chamber.
A first embodiment will be described hereinafter with reference to
More specifically, as shown in
When the air conditioner 1 operates in the cooling mode, the four-way valve 3 is switched such that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, a high-temperature and high-pressure vapor-phase refrigerant compressed by the rotary compressor 2 is guided to the outdoor heat exchanger 4 that functions as a radiator (condenser) through the four-way valve 3.
The vapor-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with air and changed to a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is decompressed in the process of passing through the expansion device 5 and changes to a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 that functions as a heat absorber (evaporator), and exchanges heat with air in the process of passing through the indoor heat exchanger 6.
As a result, the gas-liquid two-phase refrigerant takes heat from the air and evaporates, and changes to a low-temperature and low-pressure vapor-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by latent heat of vaporization of the liquid-phase refrigerant, becomes cola air, and is sent to a place to be air-conditioned (cooled).
The low-temperature and low-pressure vapor-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 3 via the four-way valve 3. When the liquid-phase refrigerant that cannot be completely evaporated is mixed in the refrigerant, the liquid-phase refrigerant is separated into the liquid-phase refrigerant and the vapor-phase refrigerant by the accumulator 8. The low-temperature and low-pressure vapor-phase refrigerant from which the liquid-phase refrigerant is separated is sucked into the compression mechanism unit of the rotary compressor 2, and is compressed again into the high-temperature and high-pressure vapor-phase refrigerant by the rotary compressor 2 and discharged to the circulation circuit 7.
In contrast, when the air conditioner 1 operates in the heating mode, the four-way valve 3 is switched such that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. For this reason, the high-temperature and high-pressure vapor-phase refrigerant discharged from the rotary compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 and exchanges heat with the air passing through the indoor neat exchanger 6. That is, the indoor heat exchanger 6 functions as a condenser.
As a result, the vapor-phase refrigerant passing through the indoor heat exchanger 6 is condensed by heat exchange with air and changed to a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is heated by heat exchange with the vapor-phase refrigerant, becomes warm air, and is sent to a place to be air-conditioned (heated).
The nigh-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the expansion device 5, and is decompressed in the process of passing through the expansion device 5 to change to a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 that functions as an evaporator, and evaporates by exchanging heat with air and changes to a low-temperature and low-pressure vapor-phase refrigerant. The low-temperature and low-pressure vapor-phase refrigerant that has passed through the outdoor heat exchanger 4 is guided to the accumulator S of the rotary compressor 2 via the four-way valve 3.
Next, a specific configuration of the rotary compressor 2 will be described with reference to
The sealed container 10 includes a cylindrical peripheral wall 10a and is erected along the vertical direction. Lubricating oil is stored inside a sealed container 10a. A discharge pipe 10b is provided at an upper end of the sealed container 10. The discharge pipe 10b is connected to the first port 3a of the four-way valve 3 via the circulation circuit 7.
The electric motor 11 is an example of a drive source, and is accommodated in an intermediate part of the sealed container 10 along the axial direction so as to be located above a liquid level S of the lubricating oil. The electric motor 11 is a so-called inner rotor type motor and comprises a stator 13 and a rotor 14. The stator 13 is fixed to an inner surface of the peripheral wall 10a of the sealed container 10. The rotor 14 is surrounded by the stator 13.
The compression mechanism unit 12 is accommodated in the lower part of the sealed container 10 so as to be immersed in the lubricating oil. As shown in
The rotating shaft 15 has a straight central axis O1 that is erected along the axial direction of the sealed container 10. The rotating shaft 15 includes a first journal portion 24a located at the upper part, a second journal portion 24b located at the lower end part, first to third crank portions 23a, 23b, and 23c, and a first intermediate shaft portion 25 and a second intermediate shaft portion 26 located between the first journal portion 24a and the second journal portion 24b. The first journal portion 24a, the second journal portion 24b, the first intermediate shaft portion 25, and the second intermediate shaft portion 26 are coaxially located on the central axis O1 of the rotating shaft 15. The rotor 14 of the electric motor 11 is connected to an upper end of the first journal portion 24a.
The first to third crank portions 23a, 23b, and 23c are located between the first journal portion 24a and the second, journal portion 24b. The first, to third, crank portions 23a, 23b, and 23c are disk-shaped elements each having a circular cross-section, and are arranged at intervals in the axial direction of the rotating shaft 15.
Furthermore, the first to third crank portions 23a, 23b, and 23c are eccentric with respect to the central axis O1 of the rotating shaft 15. That is, the eccentric directions of the first to third crank portions 23a, 23b, and 23c with respect to the central axis O1 are deviated by, for example, 120° in the circumferential direction of the rotating shaft 15.
The first intermediate shaft portion 25 is located between the first crank portion 23a and the second crank portion 23b on the central axis O1. The second intermediate shaft portion 26 is located between the second crank portion 23b and the third crank portion 23c on the central axis O1.
Furthermore, the second intermediate shaft portion 26 includes a third journal portion 27. The third journal portion 27 is a disk-shaped element having a circular cross-section, and is located coaxially with the central axis O1 of the rotating shaft 15. The third journal portion 27 has an outer diameter larger than that of the other portions of the second intermediate shaft portion 26, and is provided at a position offset to the side of the second crank portion 23b with respect to the third crank portion 23c.
As shown in
According to the present embodiment, the first crank portion 23a of the rotating shaft 15 is located 29a. The second crank portion 23b of the rotating shaft 15 is located at an inner diameter part of the second cylinder body 29b. The third crank portion 23c of the rotating shaft 15 is located at an inner diameter part of the third cylinder body 29c.
As shown in
Furthermore, a circular through hole 30 is formed in a central part of the first partition plate 17. The through hole 30 is located between the inner diameter part of the first cylinder body 29a and the inner diameter part of the second cylinder body 29b, and the first intermediate shaft portion 25 of the rotating shaft 15 penetrates the through hole 30.
According to the present embodiment, the first partition plate 17 is divided into a pair of disk-shaped plate elements 31a and 31b. The plate elements 31a and 31b are overlaid on each other in the axial direction of the rotating shaft 15. The axial direction of the rotating shaft 15 can be rephrased as the thickness direction of the plate elements 31a and 31b. One of the plate elements, i.e., the plate element 31a is in contact with the upper surface of the second cylinder body 29b. The other plate element, i.e., the plate element 31b is in contact with the lower surface of the first cylinder body 29a.
The second partition plate 13 is interposed between the second cylinder body 29b and the third cylinder body 29c. The upper surface of the second partition plate 13 is in contact with the lower surface of the second cylinder body 29b so as to cover the inner diameter part of the second cylinder body 29b from below. The lower surface of the second partition plate 18 is in contact with the upper surface of the third cylinder body 21c so as to cover the inner diameter part of the third cylinder body 21c from above.
According to the present embodiment, a thickness dimension T2 of the second partition plate 18 is larger than a thickness dimension T1 of the first partition plate 17. Furthermore, the second partition plate 13 is divided into a pair of disk-shaped plate elements 32a and 32b. The plate elements 32a and 32b are overlaid on each other in the axial direction of the rotating shaft 15. The axial direction of the rotating shaft 15 can be rephrased as the thickness direction of the plate elements 32a and 32b. One of the plate elements, i.e., the plate element 32a is in contact with the lower surface of the second cylinder body 29b. The other plate element, i.e., the plate element 32b is in contact with the upper surface of the third cylinder body 29c.
According to the present embodiment, the plate element 32a of the second partition plate 18 is formed to be thicker than the plate element 32b. As shown in
The bearing hole 33 and the communication hole 34 are located between the inner diameter part of the second cylinder body 29b and the inner diameter part of the third cylinder body 29c, and the second intermediate shaft portion 26 of the rotating shaft 15 penetrates the bearing hole 33 and the communication hole 34.
The third journal portion 27 provided in the second intermediate shaft portion 26 is slidably fitted in the bearing hole 33 of the second partition plate 18 in the axial direction. By this fitting, the second partition plate 18 also functions as a third bearing that supports the rotating shaft 15 between the second cylinder body 29b and the third cylinder body 29c.
As shown in
The end plate 37 of the first bearing 19 is surrounded by a ring-shaped support frame 33. The support frame 38 is fixed to a predetermined position on the inner surface of the peripheral wall 10a of the sealed container 10 by, for example, means such as welding.
A first cylinder body 29a is connected to the lower surface of the support frame 38 via a plurality of fastening bolts 39 (only one shown).
Furthermore, the end plate 37 of the first bearing 19, the first cylinder body 29a, the first partition plate 17, and the second cylinder body 29b are overlaid in the axial direction of the rotating shaft 15, and are integrally connected via a plurality of fastening bolts (not shown).
The second bearing 20 is arranged below the third cylinder body 29c. The second bearing 20 includes a tubular bearing body 41 that rotatably supports the second journal portion 24b of the rotating shaft 15 in the axial direction, and a flange-shaped end plate 42 extending from one end of the bearing body 41 in the radial direction of the rotating shaft 15. The end plate 42 is overlaid on the lower surface of the third cylinder body 29c so as to cover the inner diameter part of the third cylinder body 29c from below.
The end plate 42 of the second bearing 20, the third cylinder body 29c, the second partition plate 18, and the second cylinder body 29b are overlaid in the axial direction of the sealed container 10 and integrally connected via a plurality of fastening bolts (not shown).
According to the present embodiment, a region surrounded by the inner diameter part of the first cylinder body 29a, the first partition plate 17, and the end plate 37 of the first bearing 19 defines a first cylinder chamber 43. The first crank portion 23a of the rotating shaft 15 is accommodated in the first cylinder chamber 43.
A region surrounded by the inner diameter part of the second cylinder body 29b, the first partition plate 17, and the second partition plate 18 defines a second cylinder chamber 44. The second crank portion 23b of the rotating shaft 15 is accommodated in the second cylinder chamber 44.
Furthermore, a region surrounded by the inner diameter part of the third cylinder body 29c, the second partition plate 18, and the end plate 42 of the second bearing 20 defines a third cylinder chamber 45. The third crank portion 23c of the rotating shaft 15 is accommodated in the third cylinder chamber 45.
As shown in
Furthermore, the first muffler chamber 47 has a sufficient capacity for enhancing the muffling effect, and is opened inside the sealed container 10 through a plurality of exhaust holes (not shown) included in the first muffler cover 46.
A second muffler cover 48 is attached to the second bearing 20. The second muffler cover 48 and the second bearing 20 cooperate with each other to define a second muffler chamber 49. The second muffler chamber 49 is attached around the second bearing 20 so as to surround the bearing body 41 of the second bearing 20, raid is separated from the third cylinder chamber 45 by the end plate 42 of the second bearing 20.
Furthermore, the second muffler chamber 49 has a sufficient capacity for enhancing the muffling effect. According to the present embodiment, the second muffler chamber 49 communicates with the first muffler chamber 47 via a discharge passage 51 extending in the axial direction of the rotating shaft 15. The discharge passage 51 continuously penetrates outer peripheral portions of the first to third cylinder bodies 29a, 29b, and 29c, and the outer peripheral portions of the first and second partition plates 17 and 13 first and second partitions so as to connect the first muffler chamber 47 and the second muffler chamber 49.
As shown in
An upper end surface of the first roller 52 is slidably inn contact with a lower surface of the end plate 37 of the first bearing IS. The lower end surface of the first roller 52 is slidably in contact with the upper surface of the first partition plate 17 around the through hole 30. The airtightness of the first cylinder chamber 43 is thereby secured.
A ring-shaped second roller 53 is fitted in the outer peripheral surface of the second crank portion 23b. The second roller 53 rotates eccentrically inside the second cylinder chamber 44, integrally with the rotating shaft 15, and a part of the outer peripheral surface of the second roller 53 cooperates with an inner peripheral surface of the inner diameter part of the second cylinder body 29b to firm a seal portion.
The upper end surface of the second roller 53 is slidably in contact with the lower surface of the first partition plate 17 around the through hole 30. The lower end surface of the second roller 53 is slidably in contact with the upper surface of the second partition plate 13 around the bearing hole 33. The airtightness of the second cylinder chamber 44 is thereby secured.
A ring-shaped third roller 54 is fitted in the outer peripheral surface of the third crank portion 23c. The third roller 54 rotates eccentrically inside the third cylinder chamber 45, integrally with the rotating shaft 15, and a part of the outer peripheral surface of the third roller 54 cooperates with the inner peripheral surface of the inner diameter part of the third cylinder body 29c to form a seal portion.
The upper end surface of the third roller 54 is slidably in contact with the lower surface of the second partition plate 18 around the communication hole 34. A lower end surface of the third roller 54 is slidably in contact with an upper surface of the end plate 42 of the second bearing 20. The airtightness of the third cylinder chamber 45 is thereby secured.
As the first refrigerant compression unit 16A is shown as a representative in
The vane 56 cooperates with the first roller 52 to partition the first cylinder chamber 43 into a suction region R1 and a compression region R2. For this reason, when the first roller 52 rotates eccentrically in the first cylinder chamber 43, the volumes of the suction region R1 and the compression region R2 of the first cylinder chamber 43 change continuously. Although not shown, each of the second cylinder chamber 44 and the third cylinder chamber 45 is also divided into a suction region R1 and a compression region R2 by a similar vane.
As shown in
As shown in
As shown in
The first discharge ports 63a and 63b have, for example, a circular opening shape. A basic port diameter L1 of the first discharge ports 63a and 63b is, for example, 13 [mm]. A minimum cross-sectional area A1 of the first discharge ports 63a and 63b determined by the port diameter L1 is, for example, 132.7 [mm2].
In the present embodiment, the minimum cross-sectional area A1 of the first discharge ports 63a and 63b is equal. However, the first discharge ports 63a and 63b may have minimum cross-sectional areas A1 different from each other.
A reed valve 64 for opening and closing the first discharge port 63a is incorporated in the recess portion 61 of the end plate 31. The reed valve 64 opens the first discharge port 63a when the pressure in the compression region R2 of the first cylinder chamber 43 reaches a predetermined value.
A reed valve 66 for opening and closing the first discharge port 63b is incorporated in the recess portion 62 of the end plate 42. The reed valve 66 opens the first discharge port 63b when the pressure in the compression region R2 of the third cylinder chamber 45 reaches a predetermined value.
As shown in
A recess portion 69 is formed on the upper surface of the plate element 31a of the first partition plate 17. Similarly, a recess portion 10 is formed on the lower surface of the plate element 32a of the second partition plate 18. Second discharge ports 71a and 71b are formed at bottoms of the recess portions 69 and 70, respectively. The second discharge port 71a formed in the plate element 31a is opened in the second cylinder chamber 44. The second discharge port 71b formed in the plate element 32a is also opened in the second cylinder chamber 44.
The second discharge ports 71a and 71b have, for example, a circular opening shape. A basic port diameter L2 of the second discharge port 11a is, for example, 6.5 [mm]. The minimum cross-sectional area A2 of the second discharge port 71a determined by the port diameter L2 is, for example, 33.2 [mm2].
In contrast, the basic port diameter L2 of the other second discharge port 71b is, for example, 13 [mm]. A minimum cross-sectional area A2 of the other second discharge port 71b determined by the port diameter L2 is, for example, 132.7 [mm2], in other words, the second discharge port 71b has a larger port diameter L2 and a larger minimum cross-sectional area A2 than the second discharge port 71a.
Therefore, in the second cylinder chamber 44, a pair of second discharge ports 71a and 71b having different sizes are provided on both sides along the thickness direction thereof.
A reed valve 72 that opens and closes the second discharge port 71a is incorporated in the recess portion 69 of the plate element 31a of the first partition plate 17. The reed valve 72 opens the second discharge port 71a when the pressure in the compression region R2 of the second cylinder chamber 44 reaches a predetermined value.
A reed valve 74 that opens and closes the second discharge port 71b is incorporated in the recess portion 70 of the plate element 32a of the second partition plate 13. The reed valve 74 opens the second discharge port 71b when the pressure in the compression region R2 of the second cylinder chamber 44 reaches a predetermined value.
Furthermore, a recess portion 77 is formed on the lower surface of the plate element 31b of the first partition plate 17. Similarly, a recess portion 78 is formed on the upper surface of the plate element 32b of the second partition plate 18. Third discharge ports 79a and 79b are formed at bottoms of the recesses 77 and 78, respectively. The third discharge port 79a formed in the plate element 31b is opened in the compression region R2 of the first cylinder chamber 43. The third discharge port 73b formed in the plate element 32b is opened in the compression region R2 of the third cylinder chamber 45.
The third discharge ports 79a and 79b have, for example, a circular opening shape. A basic port diameter L3 of the third discharge ports 73a and 79b is, for example, 6.5 [mm]. A minimum cross-sectional area A3 of the third discharge port 79a determined by the port diameter L3 is, for example, 33.2 [mm2]. The minimum cross-sectional area A3 of the third discharge port 79b is smaller than the minimum cross-sectional area A1 of the first discharge ports 63a and 63b.
Therefore, in the first cylinder chamber 43, the first discharge port 63a and the third discharge port 79a having different sizes are provided on both sides along the thickness direction thereof. Similarly, in the third cylinder chamber 45, the first discharge port 63b and the third discharge port 79b having different sizes are provided on both sides along the thickness direction thereof.
Incidentally, in the present embodiment, the minimum cross-sectional area A3 of the third discharge ports 79a and 79b is equal. However, the third discharge ports 79a and 79b may have minimum cross-sectional areas A3 different from each other.
A reed valve 81 that opens and closes the third discharge port 79a is incorporated in the recess portion 77 of the plate element 31b of the first partition plate 17. The reed valve 81 opens the third discharge port 79a when the pressure in the compression region R2 of the first cylinder chamber 43 reaches a predetermined value.
Similarly, a reed valve 83 that opens and closes the third discharge port 73b is incorporated in the recess portion 73 of the plate element 32b of the second partition plate 18. The reed valve 33 opens the third discharge port 79b when the pressure in the compression region R2 of the third cylinder chamber 45 reaches a predetermined value.
As shown in
According to the present embodiment, since the first partition plate 17 including the third muffler chamber 85 and the muffling passage 86 is located between the first cylinder body 29a and the second cylinder body 29b, the thickness is restricted. For this reason, the third muffler chamber 85 including the muffling passage 86 has a smaller capacity than the first muffler chamber 47 and the second muffler chamber 49.
The recess portions 70 and 78 of the second partition plate 18 cooperate with each other to define a fourth muffler chamber 87 as an intermediate muffler chamber inside the second partition plate 18. The fourth muffler chamber 87 is made to communicate with the discharge passage 51 through a muffling passage 38 formed inside the second partition plate 18. The muffling passage 38 is located around the bearing hole 33 of the second partition plate 16.
According to the present embodiment, the second partition plate 13 that rotatably supports the third journal portion 27 of the rotating shaft 15 is formed to be thicker than the first partition plate 17 having no bearing function. For this reason, the depth of the recess portion 70 can be sufficiently secured by making the plate element 32a having the bearing hole 33 thicker than the other plate elements 31a, 31b, and 32b.
Therefore, in the present embodiment, the capacity of the fourth muffler chamber 87 including the muffling passage 88 is smaller than the capacities of the first muffler chamber 47 and the second muffler chamber 49, but larger than the capacity of the third muffler chamber 85 including the third muffler chamber 86.
In such a three-cylinder rotary compressor 2, when the rotating shaft 15 is driven by the electric motor 11, the first to third rollers 52, 53, and 54 eccentrically rotate in the first to third cylinder chambers 43, 44, and 45. As a result, the volumes of the suction region R1 and the compression region R2 of the first to third cylinder chambers 43, 44, and 45 change, and the vapor-phase refrigerant in the accumulator 8 is sucked into the suction regions R1 of the first to third cylinder chambers 43, 44, and 45 through the three branch pipes 59a, 59b, and 59c.
The vapor-phase refrigerant sucked into the suction region R1 of the first cylinder chamber 43 is gradually compressed in the process in which the suction region R1 shifts to the compression region R2. When the pressure of the compressed vapor-phase refrigerant reaches a predetermined value, the reed valves 64 and 81 are opened and the first discharge port 63a and the third discharge port 79a are opened.
For this reason, the vapor-phase refrigerant compressed in the first cylinder chamber 43 is discharged from the first discharge port 63a to the first muffler chamber 47, and also discharged from the third discharge port 79a to the third muffler chamber 85. The vapor-phase refrigerant discharged to the third muffler chamber 85 is guided to the first muffler chamber 47 through the muffling passage 86 and the discharge passage 51 to merge with the vapor-phase refrigerant discharged from the first discharge port 63a in the first muffler chamber 47.
The vapor-phase refrigerant sucked into the suction region R1 of the second cylinder chamber 44 is gradually compressed in the process in which the suction region R1 shifts to the compression region R2. When the pressure of the compressed vapor-phase refrigerant reaches a predetermined value, the reed valves 72 and 74 are opened and the second discharge ports 71a and 71b are opened.
For this reason, the vapor-phase refrigerant compressed in the second cylinder chamber 44 is discharged to the third muffler chamber 35 through the second discharge port 71a and also discharged to the fourth muffler chamber 87 through the second discharge port 71b. The vapor-phase refrigerant discharged into the third muffler chamber 85 is guided to the first muffler chamber 47 through the muffling passage 86 and the discharge passage 51. The vapor-phase refrigerant discharged into the fourth muffler chamber 87 is guided to the first muffler chamber 47 through the muffling passage 88 and the discharge passage 51.
The vapor-phase refrigerant sucked into the suction region R1 of the third cylinder chamber 45 is gradually compressed in the process in which the suction region R1 shifts to the compression region R2. When the pressure of the compressed vapor-phase refrigerant reaches a predetermined value, the reed valves 66 and 83 are opened and the first discharge port 63b and the third discharge port 79b are opened. For this reason, the vapor-phase refrigerant compressed in the third cylinder chamber 45 is discharged from the first discharge port 63b to the second muffler chamber 49 and also discharged from the third discharge port 79b to the fourth muffler chamber 87. The vapor-phase refrigerant discharged into the second muffler chamber 49 is guided to the first muffler chamber 47 through the discharge passage 51. The vapor-phase refrigerant discharged into the fourth muffler chamber 37 is guided to the first muffler chamber 47 through the muffling passage 83 and the discharge passage 51.
According to the present embodiment, a part of the vapor-phase refrigerant compressed in the first cylinder chamber 43 and a part of the vapor-phase refrigerant compressed in the second cylinder chamber 44 are discharged from the third discharge port 79a and the second discharge port 71a to the common third muffler chamber 85.
Similarly, a part of the vapor-phase refrigerant compressed in the third cylinder chamber 45 and the rest of the vapor-phase refrigerant compressed in the second cylinder chamber 44 are discharged from the third discharge port 79b and the second discharge port 71b to the common fourth muffler chamber 87.
In other words, the vapor-phase refrigerant compressed in the first to third cylinder chambers 43, 44, and 45 is discharged from both sides along the thickness direction, of the first to third cylinder chambers 43, 44, and 45, respectively.
At this time, since the eccentric directions of the first to third crank portions 23a, 23b, and 23c of the rotating shaft 15 are deviated by 120° in the circumferential direction of the rotating shaft 15, an equivalent phase difference is made at the timing at which the vapor-phase refrigerant compressed in the first to third cylinder chambers 43, 44, and 45 is discharged.
For this reason, the vapor-phase refrigerant discharged from the first cylinder chamber 43 to the third muffler chamber 85 and the vapor-phase refrigerant discharged from the second cylinder chamber 44 to the third muffler chamber 65 do not interfere with each other in the third muffler chamber 85. Similarly, the vapor-phase refrigerant discharged from the third cylinder chamber 45 to the fourth muffler chamber 67 and the vapor-phase refrigerant discharged from the second cylinder chamber 44 to the fourth muffler chamber 87 are the fourth. They do not interfere with each other in the muffler chamber 87.
Therefore, the vapor-phase refrigerant discharged into the third, muffler chamber 65 and the fourth muffler chamber 37 is guided to the first muffler chamber 47 through the discharge passage 51 without causing a large loss.
The vapor-phase refrigerant discharged to the second to fourth muffler chambers 49, 85, and 87 merges with the vapor-phase refrigerant discharged from the first discharge port 63a in the first muffler chamber 47, and then continuously discharged from an exhaust hole of the first muffler cover 46 into the sealed container 10. The vapor-phase refrigerant discharged into the sealed container 10 passes through the electric motor 11 and is guided from the discharge pipe 10b to the four-way valve 3.
According to the first embodiment, the first partition plate 17 and the second partition plate 13 sandwiching the intermediate second cylinder chamber 44 located between the first cylinder chamber 43 and the third cylinder chamber 45 comprise the second discharge ports 71a and 71b that open into the second cylinder chamber 44, and the third muffler chamber 85 and the fourth muffler chamber 87 that are connected to the second discharge ports 71a and 71b, respectively.
For this reason, the vapor-phase refrigerant compressed in the second cylinder chamber 44 is discharged from both sides along the thickness direction of the second cylinder chamber 44 to the third, muffler chamber 85 and the fourth muffler chamber 87 through the pair of discharge ports 71a and 71b. Therefore, although the thicknesses of the first partition plate 17 and the second partition plate 13 that sandwich the second cylinder chamber 44 are limited, the flow rate of the vapor-phase refrigerant discharged from the second cylinder chamber 44 can be increased and the discharge loss and discharge pressure pulsation of the vapor-phase refrigerant can be reduced.
Moreover, in the first embodiment, the first discharge port 63a formed on the first bearing 19 and the third discharge port 79a formed on the first chamber 43. For this reason, the vapor-phase refrigerant compressed in the first cylinder chamber 43 is discharged from the first discharge port 63a and the third discharge port 79a to both the first muffler chamber 47 and the third muffler chamber 85.
In addition, since the first discharge port 63b formed on the second bearing 20 and the third discharge port 79b formed on the second partition plate 18 are opened in the third cylinder chamber 45, the vapor-phase refrigerant compressed in the cylinder chamber 45 is discharged from the first discharge port 63b and the third discharge port 79b to both the second muffler chamber 49 and the fourth muffler chamber 37.
As a result, ail the vapor-phase refrigerant compressed in the first to third cylinder chambers 43, 44, and 45 is discharged from the two discharge ports, and the passage resistance and the discharge pressure pulsation are suppressed to a low level when the vapor-phase refrigerant passes through each of the discharge ports. Therefore, the vapor-phase refrigerant compressed in the first to third cylinder chambers 43, 44, and 45 can be discharged more efficiently, and a high-performance rotary compressor 2 can be obtained.
At the same time, each of the region from the third muffler chamber 85 to the muffling passage 66 of fourth muffler chamber 67 to the muffling passage 88 of the second partition plate 18 can be used as space for muffling. For this reason, the noise generated when the compressed, vapor-phase refrigerant flows can be reduced, and quiet operation can be performed.
As shown in
Therefore, the discharge flow rate of the vapor-phase refrigerant discharged on both sides along the thickness direction of the first to third cylinder chambers 43, 44, and 45 can be made different from each other, in each of the first to third cylinder chambers 43, 44, and 45.
More specifically, in the first embodiment, the first muffler chamber 47 attached to the first bearing 19 and the second muffler chamber 49 attached to the second bearing 20 have a larger capacity than that of the third muffler chamber 85 inside the first partition plate 17 and the fourth muffler chamber 87 inside the second partition plate 18.
Therefore, by designing the first discharge ports 63a and 63b that open to the first muffler chamber 47 and the second muffler chamber 49 to be larger than the third discharge ports 79a and 79 that open to the third muffler chamber 85 and the fourth muffler chamber 37, the flow rate of the vapor-phase refrigerant discharged from the first discharge ports 63a and 63b and the third discharge ports 79a and 79b can be optimized so as to correspond to the capacities of the first to fourth muffler chambers 47, 49, 85, and 37.
Furthermore, when the first discharge ports 63a and 63b nave a size corresponding to the capacities of the first muffler chamber 47 and the second muffler chamber 49, the flow rate of the vapor-phase refrigerant discharged from the first cylinder chamber 43 and the third cylinder chamber 45 can be secured even if the third discharge ports 79a and 79b that open in the third muffler chamber 85 and the fourth muffler chamber 87 having a small capacity than the first muffler chamber 47 and the second muffler chamber 49 are downsized.
Therefore, the vapor-phase refrigerant compressed in the first and third cylinder chambers 43 and 45 can be discharged efficiently, which is more convenient for improving the performance of the rotary compressor 2.
In addition, since the second partition plate 13 having a bearing function is formed to be thicker than the first partition plate 17 through which the rotating shaft 15 only penetrates, the capacity of the fourth muffler chamber 87 can be increased as compared with the capacity of the third muffler chamber 85.
In particular, in the present embodiment, the total value of the minimum cross-sectional area A2 of the second discharge port 71a and the minimum cross-sectional area A3 of the third discharge port 79a, which are formed on the first partition plate 17, is 66.4 [mm2]. In contrast, the total value of the minimum cross-sectional area A2 of the second discharge port 71b and the minimum cross-sectional area A3 of the third discharge pert 79b, which are formed on the second partition plate 18, is 165.9 [mm2], As a result, the flow rate of the vapor-phase refrigerant discharged to the fourth muffler chamber 87 having a large capacity can be increased, and the inside of the second partition plate 18 can be effectively utilized as a flow path for the vapor-phase refrigerant.
As shown in
As a result, the flow path of the refrigerant from the fourth muffler chamber 87 to the first muffler chamber 47 becomes much longer than the flow path of the refrigerant from the third muffler chamber 85 to the first muffler chamber 47. In other words, the capacity of the flow path of the refrigerant increases, but the flow path resistance applied to the vapor-phase refrigerant increases as the flow path becomes longer. As a result, the discharge pressure pulsation of the vapor-phase refrigerant flowing from the fourth muffler chamber 81 to the first muffler chamber 47 is suppressed and the muffling effect can be enhanced.
Furthermore, in the first embodiment, as described above, the total value of the minimum cross-sectional area A2 of the second discharge port 71b and the minimum cross-sectional area A3 of the third discharge port 79b, which are formed on the second partition plate 18, is larger than the total value of the minimum cross-sectional area A2 of the second discharge port 71a and the minimum cross-sectional area A3 of the third discharge port 79a, which are formed on the first partition plate 17.
Thus, the flow rate of the vapor-phase refrigerant discharged to the fourth muffler chamber 87 located on the side far from the first muffler chamber 47 can be increased, and a high-performance rotary compressor 2 can be obtained while increasing the capacity of the flow path and suppressing the noise during the operation.
In the second embodiment, as shown in
Furthermore, the basic port diameter L2 and the minimum cross-sectional area A2 of the second discharge port 71b formed on the second partition plate 18 are set to be equivalent to, for example, the basic port diameter L3 and the minimum cross-sectional area A3 of the third discharge ports 79a and 79b.
For this reason, the total value of the minimum cross-sectional region A2 of the second discharge port 71a and the minimum cross-sectional region A3 of the third discharge port 79a, which are formed on the first partition plate 17, is 66.4 [mm2]. In contrast, the total value of the minimum cross-sectional region A2 of the second discharge port 71b and the minimum cross-sectional region A3 of the third discharge port 79b, which are formed on the second partition plate 18, is 165.9 [mm2].
As a result, the flow rate of the vapor-phase refrigerant discharged to the third muffler chamber 85 located on the side near the first muffler chamber 47 where the vapor-phase refrigerant discharged from the first to third cylinder chambers 43, 44, and 45 merges can be increased.
Furthermore, since the third muffler chamber 85 is adjacent to the first muffler chamber 47 with the first cylinder body 29a provided therebetween, the flow path of the refrigerant from the third muffler chamber 85 to the first muffler chamber 47 is significantly shorter than the flow path of the refrigerant from the fourth muffler chamber 87 to the first muffler chamber 47.
As a result, the high-performance rotary compressor 2 capable of suppressing the flow path loss of the vapor-phase refrigerant from the third muffler chamber 85 to the first muffler chamber 47 and increasing the flow rate of the vapor phase refrigerant can be obtained.
In the third embodiment, as shown in
Similarly, the basic port diameter L2 and the minimum cross-sectional area A2 of the second discharge port lib formed on the second partition plate 18 are set to be intermediate values between the basic port diameter L1 and the minimum cross-sectional area A1 of the first discharge ports 63a and 63b, and the basic port diameter L3 and the minimum cross-sectional area A3 of the third discharge ports 79a and 79b, respectively.
More specifically, the minimum cross-sectional area A2 of the second discharge ports 71a and 71b is, for example, 60.3 [mud]. Therefore, the minimum cross-sectional area A1 of the first discharge ports 63a and 63b, the minimum cross-sectional area A2 of the second discharge ports 71a and 71b, and the minimum cross-sectional area A3 of the third discharge ports 79a and 79b meet a relationship A1>A2>A3.
As a result, the second discharge ports 71a and 71b that open in the second cylinder chamber 44 between the first cylinder chamber 43 and the third cylinder chamber 45 have an opening shape smaller than the first discharge ports 63a and 63b and larger than the third discharge ports 79a and 79b.
According to the third embodiment, the first partition plate 17 and the second partition plate 18 sandwiching the second cylinder chamber 44 include the smallest third discharge ports 79a and 79b and the second discharge ports 71a and 71b having an intermediate size. The second discharge ports 71a and 71b having an intermediate size are opened in the second cylinder chamber 44, and the smallest third discharge ports 79a and 79b are opened to both the first cylinder chamber 43 and the third cylinder chamber 45.
According to this configuration, the largest first discharge ports 63a and 63b and the smallest third discharge ports 79a and 79b open in the first cylinder chamber 43 and the third cylinder chamber 45, respectively, and the second discharge ports 71a and 71b having an intermediate size open in the second cylinder chamber 44.
Therefore, the flow rate of the vapor-phase refrigerant discharged from the first discharge ports 63a and 63b, the second discharge ports 71a and 71b, and the third discharge ports 79a and 79b can be optimized to correspond to the capacities of the first to fourth muffler chambers 47, 49, 85, and 87. Therefore, the vapor-phase refrigerant compressed in the first to third cylinder chambers 43, 44, and 45 can be discharged more efficiently, and the performance of the rotary compressor 2 can be enhanced.
In addition, since the second partition plate 18 having a bearing function is formed to be thicker than the first first partition plate 17 through which the rotating shaft 15 only penetrates, the capacity of the fourth muffler chamber 87 can be made larger than the capacity of the third muffler chamber 85. For this reason, there is an advantage that the flow rate of the vapor-phase refrigerant discharged to the fourth muffler chamber 87 having a large capacity can be increased by making the second discharge port 71b opened in the fourth muffler chamber 87 larger than the third discharge port 79b, which effectively contributes to improvement of the performance of the rotary compressor 2.
In the above embodiments, the opening shape of the discharge port is a circular shape. However, the opening shape of the discharge port is not particularly limited, but may be, for example, a polygonal shape or a D shape in which an are and a straight line are combined.
In the above embodiments, the three-cylinder rotary compressor including three cylinder chambers has been described. However, the embodiments can also be applied to, for example, a rotary compressor having four or more cylinder chambers, similarly.
Furthermore, in the above embodiments, an example of a general rotary compressor in which the vane advances in the cylinder chamber following the eccentric rotation of the roller or moves in the direction of retreating from the cylinder chamber has been described. However, the embodiments can also be applied to, for example, a so-called swing-type rotary compressor in which vanes are made to integrally project from the outer peripheral surface of the roller toward the radial outer side of the roller.
While certain embodiments have been described, these embodiments have been presented by way of example only, and are not intended to limit the scope of the inventions. Indeed, the novel embodiments described herein may be embodied in a variety of other forms; furthermore, various omissions, substitutions and changes in the form of the embodiments described herein may be made without departing from the spirit of the inventions. The accompanying claims and their equivalents are intended to cover such forms or modifications as would fall within the scope and spirit of the inventions,
This application is a Continuation Application of POT Application No. PCT/JP2018/034269, filed Sep. 14, 2013, the entire contents of which are incorporated herein by reference. Embodiments described herein relate generally to a multi-cylinder rotary compressor and a refrigeration cycle apparatus comprising the rotary compressor.
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| Number | Date | Country |
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| Number | Date | Country | |
|---|---|---|---|
| 20210190072 A1 | Jun 2021 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/JP2018/034269 | Sep 2018 | WO |
| Child | 17196301 | US |
