JP6267360B2 - Rotary compressor and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to a rotary compressor that compresses a working fluid such as a gas refrigerant and a refrigeration cycle apparatus including the rotary compressor.

2. Description of the Related Art Conventionally, a rotary compressor that compresses a working fluid such as a gas refrigerant forms a cylinder chamber in a cylinder by closing both ends of the cylinder with a closing member, and a blade that reciprocates with a roller that rotates eccentrically in the cylinder chamber. Thus, the suction chamber and the compression chamber are divided into two, the working fluid sucked into the suction chamber is compressed in the compression chamber, and the compressed working fluid is discharged from a discharge port formed in the closing member. In recent years, there is a need for such a rotary compressor to increase the amount of working fluid to be compressed at a time to increase the capacity and improve the performance. In order to meet this demand, there has been considered one that discharges a working fluid compressed in a compression chamber from a plurality of discharge ports.
For example, in the rotary compressor described in Patent Document 1 below, when a discharge port provided with a discharge valve is formed on each of the closing members located on both sides of the cylinder, the pressure in the compression chamber rises to a predetermined pressure. The discharge valve is opened to discharge the working fluid from each discharge port. This reduces the amount of working fluid that passes through each discharge port, reduces the compression loss due to over-compression caused by the flow path resistance when the working fluid passes through the discharge port, and improves the compression performance. .

JP2013-83245A

  However, when compressed working fluid is discharged from a plurality of discharge ports of the same diameter at the same time, the discharge pressure pulsation resonates and noise increases, compression loss due to the opening and closing timing of the discharge valve increases, and performance is increased. It tends to decrease. Therefore, simply providing two discharge ports cannot sufficiently improve the compression performance, and there is a reality that practical use is difficult. Moreover, the rotary compressor described in Patent Document 1 has a larger discharge port diameter provided in the bearing than a discharge port diameter provided in the partition plate, branches the flow path of the working fluid, Although the configuration is such that the working fluid flows, there is a problem that the bearing portion has lower sound insulation than the partition plate, and noise increases when a large amount of refrigerant is discharged to this portion.

  The object of the present invention is to increase the opening area of the discharge port of the partition plate larger than that of the bearing discharge port and relatively increase the amount of working fluid flowing to the partition plate in view of the above-mentioned problems of the prior art. Rotating compressor and refrigeration that can improve the overall reliability by reducing the amount of wear and reducing deformation of the sliding parts by improving the sound insulation and suppressing the high temperature on the auxiliary bearing side, thereby suppressing the deformation and increasing the efficiency. A cycle device is provided.

A rotary compressor provided to achieve the above object includes a hermetic case, a plurality of cylinders partitioned by a partition plate in the hermetic case and having a suction port and a cylinder chamber, and arranged in the cylinder chamber for eccentric rotation. It is a rotary compressor including a compression mechanism portion composed of a given roller, each forming a compression chamber in the cylinder chamber, and the compression mechanism portion includes a partition plate and a bearing that closes the cylinder. Discharge ports for discharging the working fluid compressed in the compression chamber are provided, and the opening area of the discharge port provided in the partition plate is formed larger than the opening area of the discharge port provided in the bearing. It is characterized by that.
In the rotary compressor having the above-described characteristics, a discharge valve for opening and closing the two discharge ports provided for each of the compression chambers is provided, and the discharge valves are configured to be opened with different differential pressures. Is desirable.
The discharge valve that opens and closes the discharge port provided in the partition plate is preferably the discharge valve that has a different natural frequency from the discharge valve provided in the bearing.
The discharge valve that is opened with a different differential pressure is set so that the natural frequency of the discharge valve that opens with a small differential pressure is larger than the natural frequency of the discharge valve that opens with a large differential pressure. It is desirable to do.
In addition, a refrigeration cycle apparatus provided to achieve the above-described problems includes a rotary compressor having the above characteristics, a condenser connected to the rotary compressor and condensing refrigerant discharged from the compressor body, An expansion device connected to the condenser and depressurizing the condensed refrigerant; and an evaporator for evaporating the refrigerant expanded by the expansion device. The evaporator and the compressor main body are connected by a working fluid flow path. It is connected.

According to the rotary compressor of the embodiment of the present invention having the above characteristics, the opening area of the discharge port of the partition plate is made larger than that of the bearing discharge port, and the amount of working fluid flowing to the partition plate is relatively increased. As a result, the sound insulation is improved, and it is possible to suppress the high temperature on the auxiliary bearing side in the compressor body. Therefore, the amount of wear on the sliding portion is reduced and its deformation is suppressed, and the refrigerant is highly efficient. Therefore, the reliability of the compressor and the entire refrigeration cycle apparatus can be improved.
Further features and operational effects of the present invention will become more apparent from the description of preferred embodiments described below with reference to the accompanying drawings.

These are the block diagrams which show the whole refrigeration cycle apparatus provided with the rotary compressor by the 1st Embodiment of this invention, and show the rotary compressor by sectional drawing. These are principal part sectional drawings which show the structure of the compression chamber of the rotary compressor in FIG. FIG. 2 is a schematic cross-sectional view of a compression mechanism portion in FIG. 1.

Hereinafter, embodiments for carrying out the invention will be described. In the following description, terms indicating up and down, left and right, and equal directions are used based on the illustrated state.
(First embodiment)
A rotary compressor according to a first embodiment and a refrigeration cycle apparatus including the rotary compressor will be described with reference to FIGS. 1 to 3.
FIG. 1 shows the overall configuration of a refrigeration cycle apparatus. The refrigeration cycle apparatus 1 includes a compressor body 2 and a high-pressure / high-temperature working fluid that is connected to the compressor body 2 and discharged from the compressor body 2. A condenser 3 that condenses the gas refrigerant into a liquid refrigerant, an expansion device 4 that is connected to the condenser 3 to depressurize the liquid refrigerant, an evaporator 5 that evaporates the liquid refrigerant expanded in the expansion device 4, And an accumulator 6 for separating the refrigerant into a gas phase and a liquid phase. The accumulator 6 and the compressor main body 2 are connected by a suction flow path 8 through which a working fluid flows to constitute a rotary compressor.

  The compressor body 2 has a sealed case 7 formed in a cylindrical shape. In the sealed case 7, an electric motor unit 9 located on the upper side, a rotary shaft 10 connected to the motor unit 9, and a rotary shaft A compression mechanism unit 11 driven by the electric motor unit 9 via 10 is accommodated. Lubricating oil is accommodated in the lower part of the sealed case 7.

  The electric motor unit 9 includes a rotor 12 to which the rotating shaft 10 is fixed, and a stator 13 that is fixed to the sealed case 7 and arranged at a position surrounding the rotor 12. The rotor 12 is provided with a permanent magnet (not shown), and the stator 13 is wound with an energizing coil (not shown). When the coil is energized, the rotor 12 and the rotating shaft 10 rotate.

The compression mechanism part 11 is a part which compresses the gas refrigerant which is a working fluid, and has the two cylinders 14 and 15 adjacent to an up-down direction. Between the cylinders 14 and 15, a partition plate 24 having a partition plate internal space 23 is provided as one closing member of the cylinders 14 and 15.
Of the two cylinders 14, 15, a sub bearing 18, which is the other closing member, is provided on the opposite side of the cylinder 14 positioned on the lower side from the side where the partition plate 24 is provided. A main bearing 19 which is the other closing member is provided on the opposite side of the cylinder 15 located on the upper side to the side where the partition plate 24 is provided. The cylinder chamber 16 is formed inside the cylinder 14 by closing both ends of the cylinder 14 in the vertical direction with the partition plate 24 and the auxiliary bearing 18. Similarly, the cylinder chamber 17 is formed inside the cylinder 15 by closing both ends in the vertical direction of the cylinder 15 with the partition plate 24 and the main bearing 19.

  The auxiliary bearing 18 and the main bearing 19 support the rotary shaft 10, and the rotary shaft 10 is inserted into the cylinder 14 and the cylinder 15. An eccentric portion 21 that is eccentric from the center of rotation is provided in a portion of the rotating shaft 10 that is located in the cylinder chamber 16 and the cylinder chamber 17, and a roller 22 is fitted to the eccentric portion 21. The roller 22 is arranged to rotate eccentrically while bringing the outer peripheral surface into line contact with the inner peripheral surfaces of the cylinders 14 and 15 through an oil film when the rotary shaft 10 rotates. The blade 20 will be described later with reference to FIG.

  The partition plate 24 is formed by connecting two of the first divided partition plate 24 a and the second divided partition plate 24 b that are overlapped in the axial direction of the rotary shaft 10. When the first and second divided partition plates 24a and 24b are respectively formed with concave digging portions, and the first and second divided partition plates 24a and 24b are connected to form the partition plate 24, the first, A partition plate space 23 is formed in the partition plate 24 by combining the dug portions of the second partition plates 24a and 24b.

  The first divided partition plate 24 a is formed with a partition plate discharge port 25 a which is one discharge port through which the working fluid compressed in the cylinder chamber 16 is discharged into the partition plate inner space 23. Further, the first divided partition plate 24a includes a partition plate discharge valve 26a that is one discharge valve that opens and closes the partition plate discharge port 25a, and a partition plate valve presser 27a that regulates the maximum opening of the partition plate discharge valve 26a. Is installed.

  The configuration of the second divided partition plate 24b is the same as that of the first divided partition plate 24a, and is a partition plate that is one discharge port through which the working fluid compressed in the cylinder chamber 17 is discharged into the inner space 23 of the partition plate. A discharge port 25b is formed. Further, the second divided partition plate 24b includes a partition plate discharge valve 26b that is one discharge valve for opening and closing the partition plate discharge port 25b, and a partition plate valve presser 27b that regulates the maximum opening degree of the partition plate discharge valve 26b. Is installed.

  The auxiliary bearing 18 is formed with a bearing discharge port 28a through which the working fluid compressed in the cylinder chamber 16 is discharged, and further, a bearing discharge valve 29a for opening and closing the bearing discharge port 28a, and a maximum opening of the bearing discharge valve 29a. A bearing valve presser 30a for regulating the degree is attached. A sub-bearing side muffler 31 into which the working fluid discharged from the bearing discharge port 28a flows is attached to the outer peripheral portion of the sub-bearing 18.

  The main bearing 19 is formed with a bearing discharge port 28b through which the working fluid compressed in the cylinder chamber 17 is discharged, and further, a bearing discharge valve 29b for opening and closing the bearing discharge port 28b, and a maximum opening of the bearing discharge valve 29b. A bearing valve presser 30b for regulating the degree is attached. A main bearing side muffler 32 into which the working fluid discharged from the bearing discharge port 28 b flows is attached to the outer peripheral portion of the main bearing 19.

  As shown in FIG. 1, the auxiliary bearing side muffler 31 and the main bearing side muffler 32 are connected via a communication path 33 formed in the auxiliary bearing 18, the cylinder 14, the partition plate 24, the cylinder 15 and the main bearing 19. The working fluid that has been communicated with each other and has flowed into the sub-bearing side muffler 31 flows into the main bearing-side muffler 32 through the communication path 33. The main bearing side muffler 32 is formed with an outflow hole 34 through which the working fluid in the main bearing side muffler 32 flows into the sealed case 7.

  Comparing the volumes of the sub bearing side muffler 31 and the main bearing side muffler 32, the volume of the sub bearing side muffler 31 is smaller than the volume of the main bearing side muffler 32.

Here, the difference between the partition plate discharge ports 25a and 25b formed in the first divided partition plate 24a and the second divided partition plate 24b and the discharge ports 28a and 28b formed in the auxiliary bearing 18 and the main bearing 19, and Differences between the discharge valves 26a and 26b provided on the partition plates 24a and 24b and the discharge valves 29a and 29b provided on the auxiliary bearing 18 and the main bearing 19 will be described.
The difference between the partition plate discharge port 25a formed in the first divided partition plate 24a and the bearing discharge port 28a formed in the auxiliary bearing 18, the partition plate discharge valve 26a and the bearing discharge valve 29a, and the second divided partition plate The difference between the partition plate and the bearing in the partition plate discharge port 25b formed in 24b, the bearing discharge port 28b formed in the main bearing 19, and the partition plate discharge valve 26b and the bearing discharge valve 29b is the same. Hereinafter, it will be described collectively for convenience.
When the partition plate is simply referred to, the first divided partition plate 24a and the second divided partition plate 24b are not particularly distinguished and referred to as the partition plate 24, and the discharge port provided in the partition plate 24 is referred to as the partition plate discharge port 25. The discharge valve that opens and closes the port 25 is referred to as a partition plate discharge valve 26, and the valve presser that regulates the maximum opening of the partition plate discharge valve 26 is referred to as a partition plate valve presser 27. The bearing 19 is referred to as bearings 18 and 19 without particular distinction, the discharge port provided in the bearings 18 and 19 is referred to as a bearing discharge port 28, and the discharge valve that opens and closes the bearing discharge port 28 is referred to as a bearing discharge valve 29. A valve presser that regulates the maximum opening of the discharge valve is referred to as a bearing valve presser 30.

  The partition plate discharge port 25 and the bearing discharge port 28 which are two discharge ports provided for one compression chamber have different opening areas, and the opening area of the partition plate discharge port 25 is larger than the opening area of the bearing discharge port 28. Is formed. Depending on the difference in opening area, each discharge valve for opening and closing the discharge port is also different. When the working fluid flows into the compression chamber and is compressed and the compression process is completed, the pressure in the compression chamber 39 and the pressure in the partition plate inner space 23 and the sub-bearing side muffler 31 and the main bearing side muffler 32 on the discharge side are discharged. A difference in pressure occurs. Since the working fluid flows from a high pressure to a low pressure, a certain pressure difference (hereinafter referred to as a differential pressure, which means a difference between the pressure inside the compression chamber and the pressure outside the compression chamber). ) Occurs, the discharge valve opens, and the working fluid is discharged and flows.

  Here, each discharge valve is formed to be opened with a different differential pressure. For example, if a leaf spring that opens with a small differential pressure is used for the bearing discharge valve 29 and a leaf spring that does not open unless a larger differential pressure occurs is used for the partition plate discharge valve 26, the bearing discharge valve 29 is opened first. If the pressure of the compressed working fluid further increases, the difference between the pressure in the compression chamber 39 and the pressure in the partition plate inner space 23 on the discharge side also increases, and the partition plate discharge valve 26 opens. Thus, since the partition plate discharge valve 26 is opened after the bearing discharge valve 29 is opened, it is possible to prevent the two discharge valves from opening at the same timing and to prevent resonance due to the discharge pressure pulsation.

  Further, the natural frequency “f” of the partition plate discharge valve 26 is formed to have a magnitude different from the natural frequency “f” of the bearing discharge valve 29. Each natural frequency “f” can be obtained by “f = √ (K / m) ÷ 2π”. However, K is the spring constant of the discharge valves 26 and 29, and m is the mass of the opening / closing part of the discharge valves 26 and 29. In the present embodiment, as will be described later, the numerical values of K and m are different between the partition plate discharge valve 26 and the bearing discharge valve 29.

  A part of the partition plate discharge port 25 and the bearing discharge port 28 is formed at a position where part of the partition plate discharge port 25 and the bearing discharge port 28 are separated from the cylinder chambers 16 and 17 for reasons of design restrictions. A partition plate discharge notch 35 and a bearing discharge cut are provided in the inner peripheral portions of the cylinders 14 and 15 so that the entire opening areas of the partition plate discharge port 25 and the bearing discharge port 28 communicate with the cylinder chambers 16 and 17. A notch 36 is formed. Comparing these discharge notches 35 and 36, the volume of the partition plate discharge notch 35 communicating with the partition plate discharge port 25 is formed larger than the volume of the bearing discharge notch 36 communicating with the bearing discharge port 28. Yes.

FIG. 3 is a schematic cross-sectional view of the compression mechanism unit 11 described above.
A blade groove 37 is formed in the cylinders 14 and 15, and the blade 20 is accommodated in the blade groove 37 so as to be reciprocally movable. The blade 20 is urged so that the tip end abuts against the outer peripheral surface of the roller 22, and the inside of the cylinder chambers 16 and 17 is sucked by the tip end of the blade 20 coming into contact with the outer peripheral surface of the roller 22. It is partitioned into a chamber 38 and a compression chamber 39. The suction flow path 8 communicates with the suction chamber 38, and the partition plate discharge port 25 and the bearing discharge port 28 communicate with the compression chamber 39.

  The operation of the rotary compressor 2 according to this embodiment having such a configuration will be described below.

  When the electric motor unit 9 of the rotary compressor 2 is energized, the rotary shaft 10 rotates around the center line together with the rotor 12, and the compression mechanism unit 11 is driven by this rotation, and the working fluid in the cylinder chambers 16 and 17. Is compressed. When the pressure of the compressed working fluid reaches the set pressure, the partition plate discharge valve 26 and the bearing discharge valve 29 are opened, and the working fluid is discharged from the partition plate discharge port 25 and the bearing discharge port 28. The working fluid discharged from the partition plate discharge port 25 flows into the partition plate inner space 23, and the working fluid discharged from the discharge port 28 a flows into the sub-bearing side muffler 31 and then passes through the communication path 33 to be main. It flows into the bearing side muffler 32. The working fluid discharged from the discharge port 28 b flows into the main bearing side muffler 32. The working fluid that has flowed into the main bearing side muffler 32 from each discharge port flows out into the sealed case 7 through the outflow hole 34.

  The working fluid that has flowed into the sealed case 7 then flows out of the rotary compressor 2, flows in the order of the condenser 5, the expansion device 6, and the evaporator 7, returns to the rotary compressor 2, and then enters the refrigeration cycle apparatus. The refrigeration cycle operation at 1 is executed.

  Here, the compression mechanism unit 11 includes a partition plate discharge port 25 provided in the partition plate 24 as a discharge port through which the working fluid compressed in the cylinder chambers 16 and 17 (more specifically, the compression chamber 39) is discharged. The auxiliary bearing 18 and the main bearing 19 have a bearing discharge port 28 and two discharge ports for one compression chamber. The differential pressure at which the partition plate discharge valve 26 that opens and closes the partition plate discharge port 25 and the bearing discharge valve 29 that opens and closes the bearing discharge port 28 are different. For this reason, the discharge amount of the working fluid discharged from the partition plate discharge port 25 and the bearing discharge port 28 is relatively smaller than the case where all the working fluid is discharged from one discharge port. Furthermore, since the opening timing of the partition plate discharge valve 26 that opens and closes the partition plate discharge port 25 and the bearing discharge valve 29 that opens the bearing discharge port 28 are different, the working fluid flows between the partition plate discharge port 25 and the bearing discharge port. Thus, the pulsation at the time of discharge from the compressor 28 can be suppressed and resonance of the pulsation can be prevented, and noise generated from the rotary compressor 2 can be suppressed.

  As for the noise generated when the compressed working fluid is discharged from the cylinder chambers 16 and 17, the partition plate inner space 23 to be discharged is covered by the partition plate 24, and the partition plate 24 is composed of two cylinders. 14 and 15, the noise leaking out of the rotary compressor 2 can be reduced by the sound insulation effect of the partition plate 24 and the cylinders 14 and 15. Furthermore, in this embodiment, not only the flow path is bisected, but also the amount that the working fluid flows into the partition plate inner space 23 flows to the bearing because the partition plate discharge port 25 is larger than the bearing discharge port 28. Since the amount is larger than the amount, it is possible to produce a greater sound insulation effect than conventional rotary compressors and to reduce noise.

  In addition, the partition plate discharge valve 26 that opens and closes the partition plate discharge port 25 is opened with a differential pressure different from that of the bearing discharge valve 29 that opens and closes the bearing discharge port 28, so that the working fluid can be discharged even during low-speed rotation. At a stage where the amount is small, one of the discharge valves is opened first at the time of low pressure, so that pressure loss due to overcompression that occurs to open the discharge valves 26 and 29 can be reduced, and low-speed rotation is achieved. The compression performance at the time can be improved.

  Further, the natural frequency “f” of the partition plate discharge valve 26 that opens and closes the partition plate discharge port 25 is different from the natural frequency “f” of the bearing discharge valve 29 that opens and closes the bearing discharge port 28. . When the object is deformed, the natural frequency, which means the frequency that occurs because the object is deformed in the opposite direction to return to its original state and this occurs repeatedly, the higher this value, the faster the initial speed when opening the valve. The speed when closing the valve is also fast. For this reason, the responsiveness of the discharge valve with the higher natural frequency (the ability to close quickly when the pressure drops) can be improved, and the backflow of the working fluid into the cylinder chambers 16 and 17 can be prevented. Thus, the compression performance can be improved.

  Here, in order to open the discharge valve with a small differential pressure, it is necessary to reduce the spring constant “K” of the discharge valve. If the spring constant “K” is decreased, the response of the discharge valve is lowered. become. However, if the mass “m” of the opening / closing portion of the discharge valve is reduced, the natural frequency “f” can be obtained even if “K” is reduced, as can be seen from the above formula “f = √ (K / m) ÷ 2π”. "Can be increased. Therefore, for example, if the natural frequency of the bearing discharge valve 29 is set to be smaller than the natural frequency of the partition plate discharge valve 26, “m” of the bearing discharge valve 29 that opens and closes the bearing discharge port 28 having a small opening area is reduced. The bearing discharge valve 29 is made small by opening “K” with a small differential pressure, thereby reducing pressure loss due to over-compression caused by opening the bearing discharge valve 29 at low speed rotation, and at low rotation speed. The compression performance can be improved by improving the response of the bearing discharge valve 29 while improving the compression performance.

  A part of the working fluid compressed in the cylinder chamber 17 is discharged from the partition plate discharge port 25b and flows into the partition plate inner space 23, and the other part is discharged from the bearing discharge port 28b to the main bearing side. It flows into the muffler 32. The working fluid discharged from the bearing discharge port 28b and flowing into the main bearing side muffler 32 is compressed in the cylinder chamber 16, discharged from the bearing discharge port 28a, flows into the auxiliary bearing side muffler 31, and thereafter. The working fluid that has flowed into the main bearing side muffler 32 through the communication path 33 is merged with the working fluid and flows out into the sealed case 7 from the outflow hole 34 formed in the main bearing side muffler 32.

  When the opening areas of the discharge ports 25 and 28 are compared, the opening area of the bearing discharge port 28 is smaller, so the amount of the working fluid discharged from the bearing discharge port 28a and flowing into the auxiliary bearing side muffler 31 is The amount of the working fluid discharged from the partition plate discharge port 25 and the bearing discharge port 28b and flowing into the main bearing side muffler 32 is smaller. Here, the working fluid discharged from the bearing discharge port 28a and flowing into the sub-bearing side muffler 31 is high temperature, and this working fluid passes through the communication passage 33 formed in the vicinity of the cylinder chamber 16 to the main bearing. Since it flows into the side muffler 32, the working fluid in the cylinder chamber 16 is heated in the process. When the working fluid in the cylinder chamber 16 is heated by heat from the outside, the compression performance of the rotary compressor 2 is deteriorated. As described above, it is discharged from the bearing discharge port 28a and is discharged from the auxiliary bearing side muffler 31. The amount of the working fluid flowing into the cylinder is smaller than the amount of the working fluid discharged from the partition plate discharge port 25 and the bearing discharge port 28b and flowing into the main bearing-side muffler 32. Heating of the working fluid in the chamber 16 can be suppressed. Thereby, the compression performance fall of the rotary compressor 2 by the working fluid in the cylinder chamber 16 being heated from the outside can be suppressed.

  In addition, regardless of the above-described embodiment, when the same amount of working fluid as before is sent to the sub-bearing 18, if the discharge is made from the compression chamber 39 to only one discharge port, the discharge port must be enlarged. Therefore, the dug portion for mounting the discharge mechanism portion of the sub-bearing 18 protrudes to the center portion of the sub-bearing 18, and the rigidity of the sub-bearing 18 is lowered and easily deformed. However, according to the rotary compressor according to the embodiment of the present invention, since the bearing discharge port 28 is small, the discharge mechanism portion of the compression mechanism portion can be reduced. For this reason, the lower part of the rotary compressor 2 can be stabilized.

  Furthermore, since the amount of the working fluid flowing to the sub-bearing 18 is relatively small, a large amount of working fluid compressed to a high temperature and high pressure is not collected in the lower portion, so that the temperature of the lower portion of the rotary compressor 2 is more than necessary. It wo n’t go up. Therefore, the higher the temperature is, the more the portion where the auxiliary bearing 18 and the rotary shaft 10 slide wears in proportion to the total operating time. Can be suppressed.

  Further, as described above, since the amount of the working fluid flowing into the auxiliary bearing side muffler 31 is small, the volume of the auxiliary bearing side muffler 31 can be reduced. And since the volume of the auxiliary bearing side muffler 31 is reduced, the amount of stored oil can be increased without raising the oil level with respect to the lubricating oil accommodated in the hermetic case 7, and the performance of the rotary compressor can be increased. It can be maintained over a period of time.

  Further, since the discharge ports 25 and 28 are partially formed at positions away from the cylinder chambers 16 and 17, the cylinders 14 and 17 are connected so that the entire opening area of the discharge ports 25 and 28 communicates with the cylinder chambers 16 and 17. Discharge notches 35 and 36 are formed in the inner peripheral portion of 15. By forming these discharge notches 35 and 36, the working fluid compressed in the cylinder chambers 16 and 17 can be smoothly discharged from the discharge ports 25 and 28, and the working fluid is discharged from the discharge port 25. , 28 can reduce the compression loss due to overcompression caused by the flow path resistance up to 28, and the compression performance can be improved.

  Further, the volume of the discharge notches 35 and 36 is such that the volume of the discharge notch 35 communicating with the partition plate discharge port 25 having a large opening area is equal to that of the discharge notch 36 communicating with the bearing discharge port 28 having a small opening area. It is formed larger than the volume. For this reason, the total volume of the discharge notches 35 and 36 can be suppressed. Therefore, the amount of the working fluid remaining in the discharge notches 35 and 36 at the time when the discharge of the working fluid from the cylinder chambers 16 and 17 is completed can be suppressed, and the compressed working fluid is discharged to the discharge notches 35 and 36. Re-expansion loss caused by remaining in 36 can be suppressed.

  Also, a large amount of working fluid can be compressed at a time by dispersing and discharging the working fluid compressed by the compression mechanism section from the four discharge ports. Furthermore, since the load on one discharge port is also distributed, the load on the discharge valve is reduced, and the occurrence of problems such as valve cracking is relatively reduced. Therefore, high efficiency can be achieved and overall reliability can be improved.

(Second Embodiment)
In the first embodiment, the blade and roller of the compression mechanism section are described as separate members. However, according to the present invention, a swing type in which the blade and the roller are integrated may be used as the second embodiment. good.

(Third embodiment)
Further, in the above embodiment, the number of cylinders of the rotary compressor is two, but in addition to this, the same effect can be obtained even if the third embodiment is used for a type having three or more cylinders. can get.

  In addition, this invention provides the refrigerating cycle apparatus provided with the rotary compressor in each above-mentioned Example, The refrigerating cycle apparatus is a compression which has the said structure, for example, as FIG. 1 shows. A main body 2, a condenser 3 connected to the compressor main body 2 and condensed into a liquid refrigerant by condensing gas refrigerant, which is a high-pressure and high-temperature working fluid discharged from the compressor main body 2, and connected to the condenser 3 And an expansion device 4 for decompressing the liquid refrigerant, an evaporator 5 for evaporating the liquid refrigerant expanded by the expansion device 4, and an accumulator 6 for separating the refrigerant into a gas phase and a liquid phase. And the compressor main body 2 are connected by a suction flow path 8 through which a working fluid flows to constitute a rotary compressor.

  According to the rotary compressor and refrigeration cycle apparatus of at least one embodiment described above, the opening area of the discharge port of the partition plate is made larger than that of the bearing discharge port, and the amount of working fluid flowing to the partition plate is relatively Therefore, the sound insulation is improved, the wear of the sliding part is suppressed, the pressure loss due to over-compression is reduced, the compression performance during low-speed rotation is improved, and the efficiency is improved to improve the overall reliability. It becomes possible to give.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. This embodiment and its modifications are included in the invention described in the claims and their equivalents, as well as included in the scope and gist of the invention.

  DESCRIPTION OF SYMBOLS 1 ... Refrigeration cycle apparatus, 2 ... Compressor (compressor main body), 3 ... Condenser, 4 ... Expansion apparatus, 5 ... Evaporator, 6 ... Accumulator, 7 ... Sealing case, 8 ... Suction passage, 9 ... Electric motor part, DESCRIPTION OF SYMBOLS 10 ... Rotary shaft, 11 ... Compression mechanism part, 12 ... Rotor, 13 ... Stator, 14 ... Lower cylinder, 15 ... Upper cylinder, 16 ... Lower cylinder chamber, 17 ... Upper cylinder chamber, 18 ... Secondary bearing, 19 ... Main bearing, 20 ... Blade, 21 ... Eccentric part, 22 ... Roller, 23 ... Space inside partition plate, 24 ... Partition plate, 24a ... First divided partition plate, 24b ... Second divided partition plate, 25 ... Partition plate discharge port 25a, 25b ... partition plate discharge port (lower part, upper part), 26 ... partition plate discharge valve, 26a, 26b ... partition plate discharge valve (lower part, upper part), 27 ... partition plate valve retainer, 27a, 27b ... partition plate valve Presser foot (lower part, upper part), 28 ... Bearing discharge port 28a, 28b ... Bearing discharge port (lower part, upper part), 29 ... Bearing discharge valve, 29a, 29b ... Bearing discharge valve (lower part, upper part), 30 ... Bearing valve holder, 30a, 30b ... Bearing valve holder (lower part, upper part) 31 ... Sub-bearing side muffler, 32 ... Main bearing side muffler, 33 ... Communication passage, 34 ... Outlet hole, 35 ... Discharge notch (discharge notch on partition plate discharge port side), 36 ... Discharge notch (bearing discharge) Port side discharge notch), 37 ... blade groove, 38 ... suction chamber, 39 ... compression chamber

Claims (5)

A rotary compressor comprising a sealed case, a plurality of cylinders having a suction port and a cylinder chamber partitioned by a partition plate in the sealed case, and a roller disposed in the cylinder chamber and provided with eccentric rotation. Because
A compression chamber is formed in each of the cylinder chambers, and the compression mechanism section is provided with a discharge port for discharging the working fluid compressed in the compression chamber, on the partition plate and a bearing that closes the cylinder, An opening area of the discharge port provided in the partition plate is formed larger than an opening area of the discharge port provided in the bearing. The rotation according to claim 1, wherein two discharge valves for opening and closing the two discharge ports provided for each of the compression chambers are provided, and the discharge valves are opened with different differential pressures. Type compressor. The rotary compressor according to claim 1, wherein a discharge valve having a natural frequency different from that of the discharge valve provided in the bearing is used as a discharge valve for opening and closing the discharge port provided in the partition plate. The discharge valve that is opened with a different differential pressure is set such that the natural frequency of the discharge valve that opens with a small differential pressure is larger than the natural frequency of the discharge valve that opens with a large differential pressure. The rotary compressor according to claim 2. The rotary compressor according to claim 1, a condenser connected to the rotary compressor and condensing refrigerant discharged from the compressor body, and an expansion connected to the condenser and depressurizing the condensed refrigerant. A refrigeration cycle apparatus comprising: an apparatus; and an evaporator for evaporating the refrigerant expanded by the expansion apparatus, wherein the evaporator and the compressor body are connected by a working fluid flow path.

Images