JP2005207306A - Two cylinder rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor with a reverse preventing structure which prevents the backflow of refrigerant gas into a refrigerating cycle caused by the reverse of the compressor immediately after the operation of the compressor stops, and has high reliability without causing the lack of lubrication in a compression mechanism part due to the shortage of a refrigerator oil, and also provide a refrigerating cycle device. <P>SOLUTION: The compressor comprises a first vane provided in a first cylinder and partitioning the first cylinder into a high pressure chamber and a low pressure chamber, and a second vane provided in a second cylinder and partitioning the second cylinder into a high pressure chamber and a low pressure chamber, and is configured so that the first vane is provided with a spring pushed against a first rolling piston and the second vane is not provided with a spring pushed against a second rolling piston. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a two-cylinder hermetic rotary compressor used in a refrigerating and air-conditioning system such as a room air conditioner and a refrigerator.

  FIG. 7 is a longitudinal sectional view of a conventional two-cylinder rotary compressor. In the figure, the rotating shaft 3 is rotated by the electric element 2, and the rolling pistons 9 and 10 perform eccentric rotational movements in the compression chambers 14 and 15 of the first and second cylinders 4 and 5, respectively. As a result, the refrigerant gas is sucked into the compression chamber 14 through the accumulator 19 from the suction connecting pipe 21a and into the compression chamber 15 through the suction connecting pipe 21b and compressed, and the discharge ports of the main bearing 16 and the sub-bearing 17 are compressed. 23 is discharged into the sealed container 1 and flows out from a discharge pipe 18 provided in the upper part of the sealed container 1 into a refrigeration cycle constituting the refrigeration air conditioning system.

  However, in the case of the conventional two-cylinder sealed rotary compressor, the eccentric parts 7 and 8 of the rotary shaft 3 have a phase difference of 180 degrees from each other. Since the pressure difference remains between the high-pressure chamber and the low-pressure chamber, the sealing performance is deteriorated when the refrigerating machine oil is diluted with refrigerant and the viscosity is low. Refrigerant gas and refrigerating machine oil flow into the low-pressure chamber in the compression chambers 14 and 15 through the gap between the compression chambers 14 and 15, and the rotating shaft 3 is reversed.

  In addition, a first suction passage having one end opened on the inner peripheral surface and extending substantially in parallel with the intermediate partition plate is provided in one of the two upper and lower cylinders stacked via the intermediate partition plate. Some vertical cylinders have a second intake passage that branches off from the passage in an acute angle direction and opens to the inner peripheral surface of the other cylinder. (For example, see Patent Document 1)

  In addition, a check valve is provided inside the suction connecting pipe connecting the lower cylinder and the accumulator of the two upper and lower cylinders to prevent backflow of the refrigerant gas into the refrigeration cycle, and the suction connecting pipe is checked. There is also a structure in which the check valve is disposed at a right angle through the valve and the check valve has a low pressure loss. (For example, see Patent Document 2)

Japanese Utility Model Publication No. 61-33993 Japanese Utility Model Publication No. 62-203898

  The conventional two-cylinder hermetic rotary compressor is configured as described above, and the eccentric portions 7 and 8 of the rotating shaft 3 have a phase difference of 180 degrees from each other, so that the refrigerator oil is diluted with the refrigerant. If the operation is stopped when the viscosity is low, the rotary shaft 3 reverses due to the pressure difference between the high pressure chamber and the low pressure chamber of the cylinders 4 and 5, and the pressure difference is generated in the compression chambers 14 and 15. Since they occur alternately, the rotating shaft 3 reverses until the gas pressure on both the high-pressure side and the low-pressure side reaches a complete equilibrium state, and the refrigerant gas and the refrigerating machine oil in the sealed container 1 flow backward through the refrigeration cycle and flow out. End up. As a result, there is a problem that the refrigerating machine oil in the sealed container 1 is insufficient, which may lead to insufficient lubrication of the compression mechanism.

  Further, the one described in Patent Document 1 reduces the flow path area by using one suction connecting pipe connecting the compressor body and the accumulator, and the refrigerant gas from the sealed container to the accumulator when the compressor is stopped. Although the amount of refrigerating machine oil flowing back decreased, it was difficult to completely prevent the outflow.

  In addition, since the check valve is provided inside the suction connecting pipe connecting the lower cylinder and the accumulator, the number of parts is increased and the cost is increased, and the check valve has a complicated shape. It was.

  The present invention has been made to solve the above-described conventional problems, and an object thereof is to obtain a highly reliable compressor and refrigeration cycle apparatus. It is another object of the present invention to obtain a low noise compressor and refrigeration cycle apparatus by reducing noise due to reverse rotation when the compressor is stopped. In addition, a highly reliable reverse rotation prevention structure that prevents reverse flow of refrigerant gas into the refrigeration cycle due to reverse rotation of the compressor immediately after the compressor is stopped, and does not cause insufficient lubrication of the compression mechanism due to insufficient refrigerant oil. The purpose is to obtain a compressor and a refrigeration cycle apparatus.

  A two-cylinder rotary compressor according to the present invention is a two-cylinder rotary compressor in which a first rolling piston is disposed in a first cylinder and a second rolling piston is disposed in a second cylinder. A first vane that is provided in one cylinder and that partitions the first cylinder into a high pressure chamber and a low pressure chamber; and a second vane that is provided in the second cylinder and partitions the second cylinder into a high pressure chamber and a low pressure chamber. The first vane is provided with a spring that presses against the first rolling piston, and the second vane is not provided with a spring that presses against the second rolling piston.

  The present invention can suppress the unbalanced extension force of the spring acting on the eccentric portion of the rotating shaft, can prevent the rotating shaft from reversing when the compressor is stopped, and is a refrigerating and air-conditioning system for refrigerating machine oil in a sealed container Can be prevented, and a highly reliable two-cylinder rotary compressor free from oil exhaustion can be provided. Further, even when the refrigeration oil is diluted with a refrigerant and has a low viscosity, it is possible to provide a highly reliable two-cylinder hermetic rotary compressor that can prevent reversal of the rotating shaft and does not run out of oil.

Embodiment 1 FIG.
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of a two-cylinder hermetic rotary compressor representing Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view of the compression chamber of the two-cylinder hermetic rotary compressor representing the first embodiment of the present invention.

  In the figure, the electric element 2 housed in the upper part of the hermetic container 1 includes rolling cylinders 9 and 10 in an upper cylinder 4 as a first cylinder and a lower cylinder 5 as a second cylinder via a rotating shaft 3. Rotate. An intermediate partition plate 6 is provided between the upper cylinder 4 that is the first cylinder and the lower cylinder 5 that is the second cylinder, and the opening end of the upper cylinder 4 that is the first cylinder (upper cylinder) 4, the intermediate partition plate 6 and the opposite side in the axial direction are closed by the main bearing 16, and the open end of the lower cylinder 5, which is the second cylinder (the intermediate partition plate 6 and the shaft with respect to the second cylinder 5). The side opposite to the direction) is closed by a secondary bearing 17 to form compression chambers 14 and 15, respectively.

  Vanes accommodated in first and second cylinders (upper and lower cylinders) so as to be in contact with rolling pistons 9 and 10 that are integrally fitted and mounted on eccentric parts 7 and 8 that are formed integrally with rotating shaft 3. Reference numerals 11 and 12 denote springs 13 whose front ends are pressed against the outer periphery of the rolling pistons 9 and 10, and as the rolling pistons 9 and 10 rotate, the first cylinder is the upper cylinder 4 and the second cylinder is the lower cylinder. 5 is accommodated in vane grooves 4b and 5b respectively provided in the same. The vane 11 slides in the vane groove 4b, and the upper cylinder 4, which is the first cylinder, the intermediate partition plate 6, the main bearing 16, and the compression piston 14 formed by the rolling piston 9, and the high pressure chamber 14a. It is partitioned into a low pressure chamber 14b. Further, the vane 12 slides in the vane groove 5b, and a high pressure chamber 15a is formed in the compression chamber 15 formed by the lower cylinder 5, which is the second cylinder, the intermediate partition plate 6, the auxiliary bearing 17, and the rolling piston 10. It is partitioned into a low pressure chamber 15b.

  The eccentric parts 7 and 8 are formed on the rotating shaft 3 with a phase difference of 180 degrees from each other. The discharge pipe 18 sends out the high-pressure refrigerant gas discharged from the compression chambers 14 and 15 into the refrigeration cycle constituting the refrigeration air conditioning system. The suction pipe 20 connects an accumulator 19 provided adjacent to the hermetic container 1 and a refrigeration cycle, and a refrigerant is formed in each of the cylinders 14 and 15 through the first suction flow path 4a. , 15. Here, the suction connecting pipe 21 connects a first cylinder (for example, an upper cylinder) 4 which is one cylinder and the accumulator 19, and a first suction flow path provided in the upper cylinder 4 which is the first cylinder. 4 communicates. The refrigerant compressed in the compression chambers 14 and 15 in the first and second cylinders 4 and 5 is discharged from the discharge port 23 into the sealed container 1 through the discharge muffler.

  In the present embodiment, one of the two cylinders (the upper cylinder 4 that is the first cylinder and the lower cylinder 5 that is the second cylinder) is one of the cylinders (for example, the upper that is the first cylinder). The suction connection pipe 21 is inserted only into the cylinder 4), and the other cylinder (for example, the lower cylinder 5 as the second cylinder) is inserted into one cylinder (for example, the first cylinder) without the suction connection pipe 21 being inserted. A branch passage (through hole) 6a that branches from the first suction passage 4a of the upper cylinder 4) in the cylinder is provided, and the second suction in the other cylinder (for example, the lower cylinder 5 that is the second cylinder). The refrigerant is guided into the compression chamber 15 of the other cylinder (for example, the lower cylinder 5 as the second cylinder) via the flow path 5a.

  The through hole 6a, which is the branch flow path, is a through hole provided in a portion of the intermediate partition plate 6 provided between one cylinder 4 and the other cylinder 5 that is in contact with the suction flow path 4a of one cylinder. 6a, and this through hole 6a communicates with an inclined groove 5a, which is a second suction channel provided in the other cylinder, and the branched channel 6a, an inclined groove, which is a second suction channel. The refrigerant that has passed through 5a and branched from the first suction flow path 4a is taken into the compression chamber 15 in the lower cylinder 5, which is the second cylinder.

  Further, the flow passage area of the branch flow passage 6a is larger than the flow passage area of the first suction flow passage 4a provided in the one cylinder 4 into which the suction connection pipe 21 is inserted, The flow passage area of the second suction flow passage 5a is made larger than the flow passage area of the first suction flow passage 4a provided in one cylinder 4 into which the suction connection pipe 21 is inserted. For example, the first suction channel 4a, the branch channel 6a, and the second suction channel 5a are circular channels, the diameter of the first suction channel 4a is φd2, the diameter of the branch channel is φd1, If the diameter of the second suction channel 5a is φd3, then φd2 <φd1 and φd2 <φd3.

  Next, the operation will be described. When the electric element 2 is energized, the rotating shaft 3 rotates, the rolling piston 9 performs eccentric rotational movement in the compression chamber 14 of the first cylinder 4 which is one cylinder, and the second cylinder which is the other cylinder. 5, the rolling piston 10 performs an eccentric rotational movement. As a result, the refrigerant gas is sucked into the compression chamber 14 from the suction connecting pipe 21 into the first suction flow path 4a, and is taken into the compression chamber 14 of the upper cylinder 4, which is the first cylinder, and compressed. The refrigerant that has flowed into the first suction flow path 4a passes through the through hole 6a that is a branch flow path provided in the intermediate partition plate 6 and passes through the inclined groove 5a that is the second suction flow path. It is taken into the compression chamber 15 of the cylinder and compressed.

  The refrigerant gases compressed in the compression chambers 14 and 15 are mixed in the discharge muffler 50 through the discharge ports 23 provided in the main bearing 16 and the sub-bearing 17, respectively, and discharged into the sealed container 1. 1 is discharged into a refrigerating cycle constituting a refrigerating and air-conditioning system from a discharge pipe 18 provided at the upper portion of 1.

  Here, high pressure chambers 14a and 15a and low pressure chambers 14b and 15b are formed in the compression chambers 14 and 15, respectively, but when the compressor 100 in operation is stopped, the high pressure chambers 14a and 15a and the low pressure chambers 14b, 15b, there is a pressure difference between the high pressure space in the hermetic container 1 and the compression chambers 14 and 15 and the discharge port 23 due to this pressure difference when the refrigerating machine oil is diluted with refrigerant and has a low viscosity. The refrigerant gas and the refrigerating machine oil flow into the compression chambers 14 and 15 through the operation of rotating the rotary shaft 3 in reverse.

  However, the suction flow path 4a of the upper cylinder 4 serving as the first cylinder and the suction flow path (for example, the inclined groove) 5a of the lower cylinder 5 serving as the second cylinder branch from the inside of the upper cylinder 4 serving as the first cylinder. Since it is branched in the path 6 a, the refrigerant gas and the refrigerating machine oil that flow backward when the rotating shaft 3 tries to reversely join together in the suction flow path 4 a in the cylinder 4. At this time, the refrigerant gas and the refrigerating machine oil that are going to flow backward from both the compression chamber 14 and the compression chamber 15 merge in the suction flow path 4a, so that the flow resistance in the suction flow path 4a increases and the suction connection pipe The backflow to the accumulator through 21 can be suppressed.

  During normal operation, the suction flow path 5a of the lower cylinder 5 serving as the second cylinder has a structure branched from the upper cylinder 4 serving as the first cylinder by the branch flow path 6a, and therefore suction efficiency tends to deteriorate. However, the diameter φd1 of the through-hole that is the branch flow path or the diameter of the suction flow path 5a of the lower cylinder 5 that is the second cylinder is larger than the diameter φd2 of the suction flow path of the upper cylinder 4 that is the first cylinder. By setting the diameter, the suction flow path to the lower cylinder 5 as the second cylinder can be expanded, and the suction efficiency can be improved.

  As a result of changing the diameter φd1 of the branch flow path 6a to the lower cylinder 5 which is the second cylinder as a parameter, the diameter φd1 of the branch flow path 6a to the lower cylinder 5 which is the second cylinder is changed to the first cylinder. By making the diameter φd2 or more larger than the diameter φd2 of the suction flow path 4a of the upper cylinder 4 serving as the cylinder, the suction efficiency of the lower cylinder 5 serving as the second cylinder is equal to or greater than that of the upper cylinder 4 serving as the first cylinder. It was found that the inhalation efficiency of can be ensured.

  In FIG. 1, the suction connecting pipe 21 is inserted into the upper cylinder 4 as the first cylinder, and is provided in the intermediate partition plate 6 from the suction flow path 4a in the upper cylinder 4 as the first cylinder. The refrigerant is guided to the compression chamber 15 of the lower cylinder 5 serving as the second cylinder through the through hole 6a serving as the branch channel and the inclined groove 5a serving as the suction channel in the lower cylinder 5 serving as the second cylinder. On the contrary, the suction connecting pipe 21 is inserted into the lower cylinder 5 which is the second cylinder, and the suction flow path 4a of the upper cylinder 4 which is the first cylinder is placed in the lower cylinder 5 which is the second cylinder. The refrigerant may be guided into the compression chamber 14 from the suction flow path 5a through an inclined groove provided in the upper cylinder 4 as the first cylinder through the through hole 6a that is a branch flow path of the intermediate partition plate 6. Good. The suction passage 5a of the lower cylinder 5 serving as the second cylinder is designed to have a larger passage area than the suction passage 4a of the upper cylinder 4 serving as the first cylinder. Similarly, in the specification in which the suction passage 4a of the cylinder 4 has a larger passage area than the suction passage 5a of the lower cylinder 5 which is the second cylinder, it is possible to prevent reverse rotation of the rotary shaft 3 and the like. Can be obtained.

  As described above, in the two-cylinder hermetic rotary compressor shown in the present embodiment, either one of the two cylinders (the first cylinder 4 and the second cylinder 5) (for example, the first cylinder) is used. Only the suction connection pipe 21 is inserted, and a branch flow path 6a that branches into the other cylinder (for example, the second cylinder) is provided to guide the refrigerant, and the branch flow path 6a passes through the intermediate partition plate 6. By making the flow passage area of the branch flow passage 6a larger than the suction flow passage 4a provided in one cylinder (for example, the first cylinder 4) which is configured by a through hole and into which the suction connection pipe 21 is inserted, In the suction flow path 4a in the cylinder (for example, the first cylinder 4), the refrigerant gas and the refrigerating machine oil that are going to flow backward from both the cylinders 4 and 5 merge, so that the flow resistance in the suction flow path 4a is reduced. Increase The refrigerant is less likely to flow backward, and the reversal of the rotating shaft 3 can be suppressed even when the operation is stopped in a state where the refrigerant oil is diluted with the refrigerant and the viscosity is low. It is possible to provide a highly reliable two-cylinder hermetic rotary compressor that can prevent inflow into the refrigeration cycle to be configured and is less likely to cause oil exhaustion.

Embodiment 2. FIG.
Hereinafter, a two-cylinder hermetic rotary compressor representing the second embodiment of the present invention will be described. 3 is a cross-sectional view of a compressor representing Embodiment 2 of the present invention. FIG. 4 is a longitudinal sectional view of a main part of the compressor representing the second embodiment of the present invention as seen from another angle of the two-cylinder hermetic rotary compressor shown in FIG. In the figure, the same parts as those of the first embodiment, FIG. 1 and FIG.

  In the present embodiment, the suction connecting pipe 21 is inserted only into one of the first cylinder and the second cylinder, and the branch flow path 6a that branches in the cylinder is provided to the other cylinder. In addition to guiding the refrigerant, only one of the cylinders (for example, the first cylinder) is provided with a spring 13 for pressing the vane (for example, the vane 11) from the back to the rolling piston (for example, the rolling piston 9) that rotates in the cylinder, The other cylinder is not provided with a spring for pressing the vane (for example, the vane 12).

  In FIG. 3, the sealed container 1 of the two-cylinder hermetic rotary compressor has an electric element 2, a rotating shaft 3, an upper cylinder 4 that is a first cylinder, a lower cylinder 5 that is a second cylinder, and a rotating shaft 3. It is comprised from the eccentric parts 7 and 8 shape | molded integrally, the rolling pistons 9 and 10, and the vanes 11 and 12. FIG. As shown in FIG. 4, in the present embodiment, the upper cylinder 4 that is the first cylinder is provided with a spring 13 to press the vane 11 toward the rolling piston 9. Further, since a high pressure is applied to the back surface of the vane 11, the vane 11 is pressed by the high pressure. The lower cylinder 5, which is the second cylinder, is not provided with a spring that presses the vane 12 toward the rolling piston 10, and the vane 12 is only high pressure applied to the back surface.

  The operation of the two-cylinder hermetic rotary compressor configured as described above will be described below. When the electric element 2 is energized, the rotary shaft 3 rotates, and the rolling piston 9 performs eccentric rotational movement in the compression chamber 14 formed in the upper cylinder 4 that is the first cylinder, and the lower cylinder that is the second cylinder. The rolling piston 10 performs an eccentric rotational motion in a compression chamber 15 formed in the cylinder 5. As a result, the refrigerant gas is sucked into the compression chambers 14 and 15 from the refrigeration cycle constituting the refrigeration air-conditioning system through the suction connection pipe 21 and compressed.

  When the compressor in operation is stopped, a pressure difference remains between the high pressure chambers 14a and 15a and the low pressure chambers 14b and 15b. Here, in the present embodiment, in the compression chamber 14 in the upper cylinder 4 which is the first cylinder, an amplitude force is generated by the spring 13 in addition to this pressure difference, but in the lower cylinder 5 which is the second cylinder. Since there is no spring in the compression chamber 15, no force acts other than the pressure difference between the high pressure chamber 15a and the low pressure chamber 15b.

  As a result, the force acting on the eccentric portion 7 of the rotating shaft 3 in the compression chamber 14 is different from the force acting on the eccentric portion 8 of the rotating shaft 3 in the compression chamber 15, and the force for reversing the rotating shaft 3 is different. Since it becomes unbalanced, there is no reverse. Here, if the springs 13 are provided in the vanes 11 and 12 of the compression chamber 14 and the compression chamber 15 respectively, the eccentric portions 7 and 8 are provided 180 degrees apart from each other. In a very stable state, the other spring is compressed and becomes unstable, causing an unbalance in the spring, and this time the other spring that is compressed tries to stretch, so it tries to reverse. However, the rotation shaft 3 continues to rotate (reverse) forever. However, in the present embodiment, the spring 13 is provided only on one vane 11 and the spring is not provided on the other vane 12, so that the spring 13 of one cylinder 4 is fully extended. Therefore, the rotating shaft 3 is stabilized and the reverse rotation of the rotating shaft 3 is suppressed.

  In the present embodiment, a spring that presses the vane 12 is not inserted into the lower cylinder 5 that is the second cylinder. In the normal operation, when the rotating shaft 3 starts rotating, in the compression chamber 14 in the upper cylinder 4, which is the first cylinder, the vane 11 is pressed from the back to the rolling piston by the amplitude force of the spring 13, and thus the high pressure chamber 14a. And the low-pressure chamber 15a are partitioned, compressed, and discharged from the discharge port 23 into the sealed container 1 through the discharge muffler 50. The vane 12 in the lower cylinder 5 as the second cylinder is pressed from the back to the rolling piston 10 side by the high pressure in the sealed container 1 due to the high-pressure refrigerant gas discharged into the sealed container 1. Even in the lower cylinder 5, which is the cylinder, the high pressure chamber 14 b and the low pressure chamber 15 b are partitioned by the vane 12 without being provided with a spring that presses the vane 12, and compression is normally performed.

  In FIG. 4, the spring 13 is provided only in the upper cylinder 4 as the first cylinder and the spring is not provided in the lower cylinder 5 as the second cylinder, but conversely the lower cylinder as the second cylinder. Similarly, the reverse rotation of the rotary shaft 3 can be prevented even if the spring 13 is provided only in the cylinder 5 and the upper cylinder 4 as the first cylinder is not provided with a spring.

  As described above, in the two-cylinder hermetic rotary compressor of the present embodiment, the suction connection pipe 21 is inserted into only one of the two (upper and lower) cylinders, and the other cylinder is branched in the cylinder. A branch flow path 6a is provided to guide the refrigerant, and only one of the cylinders is provided with a spring that presses the vane from the back of the rolling piston that rotates in the cylinder, and the other cylinder is not provided with a spring. Yes.

  Therefore, the compression chambers 14 and 15 in the two (first and second) cylinders are formed so as to be shifted from each other by 180 degrees, so that the extension force of the spring acting on the eccentric portion of the rotating shaft is unbalanced. The balance can be suppressed, the reversal of the rotating shaft when the compressor is stopped, the refrigerating machine oil in the hermetic container 1 can be prevented from flowing into the refrigerating cycle constituting the refrigerating air conditioning system, A highly reliable two-cylinder hermetic rotary compressor without exhaustion can be provided. Further, as described in the first embodiment, even when the refrigerating machine oil is diluted with a refrigerant and in a low viscosity state, the rotation of the rotary shaft 3 can be prevented, and a highly reliable two-cylinder sealed rotation without oil depletion. A compressor can be provided.

Embodiment 3 FIG.
Hereinafter, a two-cylinder hermetic rotary compressor representing the third embodiment of the present invention will be described with reference to the drawings. FIG. 5 is a longitudinal sectional view of a compressor representing the third embodiment of the present invention. 6 is a diagram for explaining the behavior of the check valve provided in the branch flow path, FIG. 6a is a diagram showing the behavior of the check valve during normal operation, and FIG. 6b is a refrigerant gas. It is a figure showing the behavior of the check valve when the reverse flow of the refrigeration oil occurs. In the figure, the same parts as those in Embodiments 1 and 2 and FIGS. In the present embodiment, the suction connecting pipe is inserted only into one of the two (first and second) cylinders 4 and 5 (for example, the first cylinder 4), and the other cylinder (for example, the first cylinder 4). The second cylinder 5) is provided with a branch flow path 6a that branches in the cylinder to guide the refrigerant, and a check valve 24 is provided in the branch flow path 6a to prevent back flow of the refrigerant.

  In the figure, a sealed container 1 of a two-cylinder hermetic rotary compressor has an electric element 2, a rotating shaft 3, an upper cylinder 4 that is a first cylinder, a lower cylinder 5 that is a second cylinder, and a rotating shaft 3. Are formed of eccentric parts 7 and 8, rolling pistons 9 and 10, and vanes 11 and 12. The branch flow path 6a into the lower cylinder 5, which is the second cylinder, is configured at right angles via a check valve 24 and a check valve spring 25, and is configured to open and close the branch flow path 6a. ing. When the compressor 100 is stopped, the check valve 24 is pressed against the end face of the through hole 6a which is a branch flow path provided in the intermediate partition plate 6 by the amplitude force of the check valve spring 25, and is sealed. The suction flow path of the upper cylinder 4 that is one cylinder and the suction flow path in the lower cylinder 5 that is the second cylinder are partitioned.

  The operation will be described below. When the electric element 2 is energized and the rotating shaft 3 rotates, the rolling pistons 9 and 10 perform eccentric rotational movement in the compression chambers 14 and 15 of the first cylinder 4 and the second cylinder 5, respectively. As a result, the refrigerant gas is sucked into the compression chambers 14 and 15 from the refrigerating cycle constituting the refrigerating and air-conditioning system through the suction connecting pipe 21 to be compressed. At this time, as shown in FIG. 6a, during normal operation, the check valve 24 in the lower cylinder 5, which is the second cylinder, is pushed down against the check valve spring 25 by the pressure of the sucked refrigerant gas.

  Here, when the compressor 100 in operation is stopped, a pressure difference remains between the high pressure chambers 14a and 15a and the low pressure chambers 14b and 15b, so that the refrigerant gas and the refrigerating machine oil flow backward due to the pressure difference, and the rotating shaft 3 Try to reverse. In particular, when the refrigerating machine oil is in a low-viscosity state diluted with a refrigerant, the refrigerant easily leaks and easily reverses.

  However, the refrigerant gas which tends to flow backward from the second suction flow path 5a of the lower cylinder 5 as the second cylinder to the accumulator 19 via the first suction flow path 4a of the upper cylinder 4 as the first cylinder, and In the refrigeration oil, the check valve 24 is immediately pressed against the lower end surface of the intermediate partition plate 6 by the amplitude force and pressure difference of the check valve spring 25, and the branch flow path 6a provided in the intermediate partition plate 6 is closed. Further, the reverse flow of the refrigerant and the refrigerating machine oil is prevented, and further, the reverse rotation phenomenon at the time of stoppage that occurs in the two-cylinder sealed rotary compressor can be prevented.

  In FIG. 5, the suction connecting pipe 21 is inserted into the upper cylinder 4 which is the first cylinder, and the branch flow path of the intermediate partition plate 6 from the suction flow path 4a in the upper cylinder 4 which is the first cylinder. The check valve 24 and the check valve spring 25 are connected to the second cylinder of the lower cylinder 5 as the second cylinder by branching to the suction flow path of the lower cylinder 5 as the second cylinder through the through hole 6a. Although the specification is provided in the suction flow path 5a, the suction connection pipe 21 is inserted into the lower cylinder 5 which is the second cylinder, and the first suction of the upper cylinder 4 which is the first cylinder. The flow path 4a is branched from the second suction flow path in the lower cylinder 5 which is the second cylinder through the through hole 6a which is the branch flow path of the intermediate partition plate 6, and the check valve 24 and the check valve The valve spring 25 is the first cylinder Has the same effect in specifications provided in the middle first suction passage 4a of the cylinder 4, it is possible to prevent the reverse rotation of the rotary shaft 3.

  As described above, in the two-cylinder hermetic rotary compressor shown in the present embodiment, one of the two cylinders (the upper cylinder 4 that is the first cylinder and the lower cylinder 5 that is the second cylinder). The suction connecting pipe 21 is inserted only into the first cylinder 4 (for example, the first cylinder 4), and the second cylinder 5 (for example, the second cylinder 5) is provided with a second suction passage 5a that branches in the cylinder to guide the refrigerant. By providing the check valve 24 in the second suction flow path 5a, even if the refrigerant gas and the refrigerating machine oil try to flow back to the accumulator 19 through the first and second suction flow paths 4a and 5a of the cylinder, the check valve The check valve 24 is immediately pressed against the end face so as to close the through hole 6a which is the branch flow path of the intermediate partition plate 6 due to the amplitude force and pressure difference of the spring 25, so that the two-cylinder hermetic rotary compressor is used. Reversals during arrest have been caused can be prevented, it is possible to provide a highly reliable two-cylinder sealed type rotary compressor.

  In addition, as a refrigerant | coolant used in Embodiment 1-Embodiment 3, it is HFC refrigerant | coolants, such as R410A, R407C, for example, As refrigerating machine oil which lubricates a compression mechanism part, HFC type refrigerant | coolants, such as alkylbenzene, Incompatible or weakly compatible oil is used.

  When the compressor in operation stops, a pressure difference remains between the high pressure chambers 14a and 15a and the low pressure chambers 14b and 15b. The low pressure chambers 14b and 15b have the pressure in the sealed container 1 and the high pressure chambers 14a and 15a. Since the pressure is lower than the internal pressure, the high pressure refrigerant gas and the refrigerating machine oil are supplied to the low pressure chamber through the high pressure space in the sealed container 1 and the gap between the high pressure chambers 14a and 15a and the low pressure chambers 14b and 15b due to the pressure difference. 14b, 15b or the low pressure space.

  In particular, when a compatible oil that is compatible with the refrigerant is used, if the refrigerating machine oil is diluted with the refrigerant, the viscosity of the refrigerating machine oil becomes low and easily leaks, but in this embodiment, the refrigerating machine oil is an HFC such as alkylbenzene. Since the refrigerant is incompatible or weakly compatible with the refrigerant, the refrigerating machine oil is not diluted with the refrigerant, the refrigerating machine oil remains high in viscosity, the high-pressure space in the sealed container 1 and the compression chamber 14. The refrigerant gas and the refrigeration oil do not leak into the compression chambers 14 and 15 and flow into the compression chambers 14 and 15. Therefore, a reversible phenomenon due to leakage is unlikely to occur, and a highly reliable compressor with low noise that does not cause abnormal noise or bearing seizure can be obtained.

  As described above, in the two-cylinder hermetic rotary compressor of the present embodiment, the refrigerant is an HFC refrigerant such as R410A and R407C, and the refrigerator oil is incompatible or weakly compatible with an HFC refrigerant such as alkylbenzene. Therefore, it is possible to prevent a reverse rotation phenomenon at the time of stopping that occurs in the two-cylinder hermetic rotary compressor, and to provide a low-noise and high-reliability two-cylinder hermetic rotary compressor.

  As described above in the first to third embodiments, the first rolling piston 9 is disposed in the first cylinder 4 and the second rolling piston 10 is disposed in the second cylinder 5. In the two-cylinder rotary compressor, the first vane 11 is provided in the first cylinder 4 and partitions the first cylinder 4 into the high pressure chamber 14a and the low pressure chamber 14b, and the second cylinder 5 is provided. And a second vane 12 that partitions the inside of the cylinder 5 into a high pressure chamber 15a and a low pressure chamber 15b. The first vane 11 is provided with a spring 13 that presses against the first rolling piston 9, and the second vane 12 is not provided with a spring that presses against the second rolling piston 10, so that it is possible to suppress the unbalanced extension force of the spring acting on the eccentric part of the rotating shaft, and when the compressor is stopped. A reliable two-cylinder sealed rotary compressor that can prevent reversal of the rotating shaft, can prevent the refrigeration oil in the hermetic container 1 from flowing out into the refrigeration cycle constituting the refrigeration air conditioning system, and has no oil depletion. Can be provided. In addition, even when the refrigeration oil is diluted with a refrigerant and has a low viscosity, it is possible to provide a highly reliable two-cylinder hermetic rotary compressor that can prevent the rotation of the rotating shaft 3 and that does not run out of oil.

  In the two-cylinder rotary compressor in which two first and second cylinders 4 and 5 and two rolling pistons 9 and 10 are arranged in an axial direction in a sealed container, the two cylinders 4 and 5 1 is provided only in one cylinder (for example, the first cylinder 4), the refrigerant is sucked from the outside of the sealed container 1, and the first suction flow into the compression chamber 14 in one cylinder (for example, the first cylinder 4). One suction connection pipe 21 that guides the refrigerant through the path 4a and the first intake flow path 4a branch the refrigerant, and the refrigerant sucked from the suction connection pipe is compressed by the other cylinder (for example, the second cylinder 5). A second suction channel (for example, the second suction channel 5a or the branch channel 6a) leading into the chamber 15, and a channel area of the first suction channel and a second suction channel (for example, Second suction channel 5a or branch channel Since the total flow path area of a) is larger than the flow path area of the suction connecting pipe 21, the refrigerant gas and the refrigerating machine oil that are going to flow backward from both the compression chamber 14 and the compression chamber 15 are within the suction flow path 4a. By joining, the flow resistance in the suction flow path 4a is increased, the backflow to the accumulator through the suction connecting pipe 21 can be suppressed, and the reverse rotation can be suppressed.

  Further, in the two-cylinder rotary compressor in which two cylinders and two rolling pistons are arranged to overlap in the axial direction, the compressor is provided only in one of the two cylinders, and sucks refrigerant from outside the sealed container 1. A suction connection pipe 21 that guides the refrigerant to the compression chamber in one cylinder via the first suction flow path 4a, and the refrigerant branched from the first suction flow path 4a and sucked from the suction connection pipe 21 to the other A second suction flow path (for example, the second suction flow path 5a or the branch flow path 6a) leading to the compression chamber of the cylinder 5, and a second suction flow path (for example, the second suction flow path 5a or Since the check valve 24 for preventing the back flow from the second cylinder 5 side is provided in the branch flow path 6a), the check valve 24 prevents the refrigerant and the refrigerating machine oil from flowing back from the second suction flow path 5a. Yes, in a two-cylinder rotary compressor Stiff it is possible to prevent the reversal phenomenon at the time of stoppage.

  Further, in the two-cylinder rotary compressor in which the two cylinders 4 and 5 and the two rolling pistons 9 and 10 are disposed so as to overlap each other in the axial direction, only one of the two cylinders 4 and 5 is provided. A suction connection pipe that sucks the refrigerant from outside the sealed container 1 and guides the refrigerant to the compression chamber in one cylinder 4 via the first suction flow path 4a, and branches from the first suction flow path. A second suction flow path that guides the refrigerant sucked from the pipe 21 into the compression chamber of the other cylinder 5, and the flow passage area of the second suction flow path 5a is the flow path of the first suction flow path 4a. Since the area is larger than the area, the suction efficiency of the other cylinder 5 can be ensured to be equal to or higher than that of the one cylinder 4.

  Moreover, since the refrigerant is an HFC refrigerant such as R410A, R407C, and the refrigerating machine oil is an HFC refrigerant such as alkylbenzene and an incompatible or weakly compatible oil, the refrigerating machine oil is difficult to be diluted with the refrigerant, Since the viscosity remains high, refrigerant leakage is unlikely to occur, the reverse rotation phenomenon when the compressor is stopped can be prevented, and a low-noise and highly reliable two-cylinder hermetic rotary compressor can be provided. .

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a two-cylinder hermetic rotary compressor that represents Embodiment 1 of the present invention. 1 is a cross-sectional view of a two-cylinder hermetic rotary compressor that represents Embodiment 1 of the present invention. It is a longitudinal cross-sectional view of the 2-cylinder hermetic rotary compressor representing the second embodiment of the present invention. It is a principal part longitudinal cross-sectional view of the 2 cylinder sealed rotary compressor showing Embodiment 2 of this invention. It is a longitudinal cross-sectional view of the 2-cylinder hermetic rotary compressor representing the third embodiment of the present invention. It is a figure showing the behavior of the non-return valve at the time of normal operation of the 2-cylinder hermetic rotary compressor representing the third embodiment of the present invention. It is a longitudinal cross-sectional view of the conventional 2-cylinder hermetic rotary compressor.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Airtight container, 2 Electric element, 3 Rotating shaft, 4 1st cylinder, 4a Suction flow path, 4b Vane groove, 5 2nd cylinder, 5a Suction flow path, 5b Vane groove, 6 Intermediate partition plates, 7, 8 Eccentric part, 9, 10 Rolling piston, 11, 12 Vane, 13 Spring, 14, 15 Compression chamber, 14a, 15a High pressure chamber, 14b, 15b Low pressure chamber, 16 Main bearing, 17 Sub bearing, 18 Discharge pipe, 19 Accumulator, 20 suction pipe, 21, 21a, 21b suction connection pipe, 22 suction port, 23 discharge port, 24 check valve, 25 check valve spring.

Claims (5)

In a two-cylinder rotary compressor in which a first rolling piston is disposed in a first cylinder and a second rolling piston is disposed in a second cylinder, the first cylinder is provided in the first cylinder, A first vane that partitions the inside of one cylinder into a high-pressure chamber and a low-pressure chamber, and a second vane that is provided in the second cylinder and partitions the inside of the second cylinder into a high-pressure chamber and a low-pressure chamber, The two-cylinder characterized in that the first vane is provided with a spring that presses against the first rolling piston, and the second vane is not provided with a spring that presses against the second rolling piston. Rotary compressor. In a two-cylinder rotary compressor in which two cylinders and two rolling pistons are arranged in an axial direction so as to overlap each other in a sealed container, the refrigerant is provided only in one of the two cylinders, and is supplied from outside the sealed container. One suction connection pipe that guides the refrigerant to the compression chamber in the one cylinder through the first suction flow path, and branches from the first suction flow path, and is sucked from the suction connection pipe A second suction passage for guiding the refrigerant into the compression chamber of the other cylinder, and the sum of the passage area of the first suction passage and the passage area of the second suction passage is A two-cylinder rotary compressor characterized in that it is larger than the flow passage area of the suction connecting pipe. In a two-cylinder rotary compressor in which two cylinders and two rolling pistons are arranged so as to overlap in the axial direction, the compressor is provided only in one of the two cylinders, and sucks refrigerant from outside the sealed container. A suction connection pipe for introducing a refrigerant to the compression chamber in the one cylinder via a first suction flow path; and the refrigerant branched from the first suction flow path, and the refrigerant sucked from the suction connection pipe is supplied to the other cylinder A two-cylinder rotary compression according to claim 1 or 2, further comprising a check valve provided in the second suction flow path. Machine. In a two-cylinder rotary compressor in which two cylinders and two rolling pistons are arranged so as to overlap in the axial direction, the compressor is provided only in one of the two cylinders, and sucks refrigerant from outside the sealed container. A suction connection pipe for introducing a refrigerant to the compression chamber in the one cylinder via a first suction flow path; and the refrigerant branched from the first suction flow path, and the refrigerant sucked from the suction connection pipe is supplied to the other cylinder And a second suction flow path leading into the compression chamber of the cylinder, wherein the flow passage area of the second suction flow path is larger than the flow passage area of the first suction flow path. The two-cylinder rotary compressor according to any one of claims 1 to 3. The refrigerant is an HFC refrigerant such as R410A or R407C, and the refrigerating machine oil is incompatible or weakly compatible with the HFC refrigerant such as alkylbenzene. The two-cylinder rotary compressor described.

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