JP2011058431A - Hermetic rotary compressor and refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hermetic rotary compressor capable of supplying a lubricating oil of a predetermined pressure to a sliding part, supplying a lubricating oil also into a cylinder chamber, and improving the sealing property of a compression chamber so as to restrain performance degradation. <P>SOLUTION: In the hermetic rotary compressor 1, an electric motor part 3 and a compression mechanism part 4 driven by the electric motor part 3 are stored in a closed container 2, so that a refrigerant is sucked into the compression mechanism part 4 via the space inside the closed container 2. A volume type oil feeding pump device 100 is provided with the suction port immersed in a lubricating oil 99, so that the lubricating oil 99 discharged from the volume type oil feeding pump device 100 is supplied to a sliding part of the compression mechanism part 4. A lubricating oil return mechanism 50 is provided in a return path of the lubricating oil to the closed container 2 as a pressure control mechanism for controlling the pressure of the lubricating oil in the return path. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a hermetic rotary compressor and a refrigeration cycle apparatus, and more particularly to a hermetic rotary compressor and a refrigeration cycle apparatus that sucks refrigerant into a compression mechanism through a space in a hermetic container.

  A rotary compressor in which the suction pressure of the refrigerant gas is introduced into the sealed container is said to be inferior in performance and reliability as compared with a compressor in which the inside of the sealed container has a discharge pressure of the refrigerant gas. The reason for this is that when the inside of the sealed container is at the discharge pressure of the refrigerant gas, the lubricating oil sucked from the bottom of the rotating shaft and sent to the sliding portion becomes the discharge pressure, and this lubricating oil reaches the low pressure side in the cylinder chamber. It enters through a gap such as a roller and a bearing that forms a cylinder chamber, and the sealing performance of the compression chamber is maintained. On the other hand, when the inside of the sealed container is at the suction pressure of the refrigerant gas, the lubricating oil sent to the sliding portion becomes the suction pressure, and the lubricating oil is difficult to enter the cylinder chamber, so that the sealing performance of the compression chamber is deteriorated. .

  In addition, the sliding part between the vane that partitions the compression chamber and the vane groove of the cylinder has a pressure difference between the discharge pressure in the sealed container and the pressure in the cylinder chamber from the back side of the vane when the inside of the sealed container is at discharge pressure. However, if the inside of the sealed container is at suction pressure, there is no supply of lubricant due to the pressure difference, and there is a risk of wear or galling at the sliding part between the vane and the vane groove of the cylinder. . As a countermeasure to this problem, it is considered that a small hole suction port is opened in the cylinder suction pipe in the sealed container and the lubricating oil is sucked into the cylinder chamber, but the amount of oil supplied from the suction hole of the small hole of the suction pipe is It is difficult to adjust because it fluctuates greatly depending on the rotation speed of the compressor.If the rotation speed is too high, extra work to circulate the lubricating oil increases, and if the rotation speed is too low, the compression chamber will be insufficiently sealed. Reduce performance.

  Patent Document 1 proposes a rotary compressor that solves the above problem. In the compressor of Patent Document 1, an electric motor part and a compression mechanism part are housed in a sealed container, and suction gas is guided into the sealed container, and then the suction of the cylinder chamber is performed through a pipe provided outside the sealed container. Guided to the mouth. An oil separator is provided in the discharge passage outside the hermetic container, and the lubricating oil separated by the oil separator is guided to the vane chamber and the sliding portion around the rotation shaft.

JP 2006-258002 A

  In the device described in Patent Document 1, the lubricating oil is discharged from the cylinder chamber together with the refrigerant gas, separated by the oil separator, returned to the sliding portion, and circulated into the cylinder chamber through the clearance between the sliding portions. In this case, there are the following problems. That is, the lubricating oil supplied to the oil supply path of the compression mechanism section enters the cylinder chamber and also leaks into the sealed container from the clearance between the rotating shaft and the bearing and enters the lubricating oil reservoir at the bottom of the sealed container. In addition, the amount of lubricating oil circulating in the cylinder chamber, oil separator, oil supply path, and cylinder chamber gradually decreases, and there is a risk of seizure of the sliding portion and galling due to insufficient oil supply.

 In order to eliminate this inconvenience, it is described in FIG. 1 of Patent Document 1 that a small hole is formed in the suction port to the cylinder chamber and introduced into the cylinder chamber together with the suction gas. However, the amount of oil supplied from the suction port to the cylinder chamber varies greatly depending on the number of revolutions of the compressor, so adjustment is difficult.If the amount of oil supplied is too large, the oil separator becomes full and loses the separation capacity. If the amount of oil supply is too small, it will be insufficient.

  The present invention has been made in view of the above, and its purpose is the same as that of a rotary compressor in which lubricating oil having an appropriate pressure can be supplied to the sliding portion and the inside of a normal hermetic container has a discharge pressure. Another object of the present invention is to provide a hermetic rotary compressor and a refrigeration cycle apparatus in which lubricating oil is also supplied to the cylinder chamber to improve the sealing performance of the compression chamber and suppress performance degradation.

In a hermetic rotary compressor according to the present invention, an electric motor unit and a compression mechanism driven by the electric motor unit are housed in a hermetic container storing lubricating oil at the bottom, and a refrigerant is passed through the space in the hermetic container. In the hermetic rotary compressor that sucks into the compression mechanism part,
A positive displacement oil pump device is provided by immersing the suction port in the lubricant oil, the lubricant oil discharged from the positive displacement oil pump device is supplied to the sliding portion of the compression mechanism portion, and the lubricant oil A pressure control mechanism for controlling the pressure of the lubricating oil in the return passage is provided in the return passage to the sealed container. According to the above configuration, lubricating oil having an appropriate pressure higher than the refrigerant suction pressure can be supplied to the sliding portion, the lubricating oil is also supplied to the cylinder chamber, and the sealing performance of the compression chamber is improved to suppress performance deterioration. be able to.

  The refrigeration cycle apparatus of the present invention includes the hermetic rotary compressor, a condenser, an expansion device, and an evaporator. According to the above configuration, the lubricating oil having an appropriate pressure higher than the refrigerant suction pressure can be supplied to the sliding portion of the hermetic rotary compressor, and the lubricating oil is also supplied to the cylinder chamber to improve the sealing performance of the compression chamber. As a result, the performance degradation can be suppressed.

  According to the present invention, it is possible to supply a lubricating oil having an appropriate pressure to the sliding portion, to supply the lubricating oil to the cylinder chamber, and to improve the sealing performance of the compression chamber and suppress the performance degradation. A compressor and a refrigeration cycle apparatus can be provided.

It is a longitudinal section showing Embodiment 1 of a closed type rotary compressor of the present invention. The eccentric part of a cylinder chamber, a roller, and a rotating shaft is shown, FIG. 2 (A) is a top view of these elements, FIG. 2 (B) is a cross section in the AA line in FIG. 2 (A). FIG. It is sectional drawing which shows the structural example of a lubricating oil return mechanism. FIG. 4 (A) is a longitudinal sectional view showing Embodiment 2 of the present invention, and FIG. 4 (B) is a longitudinal sectional view showing Embodiment 3 of the present invention. It is a longitudinal cross-sectional view which shows Embodiment 4 of the sealed rotary compressor of this invention. It is a longitudinal cross-sectional view which shows Embodiment 5 of the sealed rotary compressor of this invention. It is a longitudinal cross-sectional view which shows Embodiment 6 of the hermetic rotary compressor of the present invention. It is a longitudinal cross-sectional view which shows Embodiment 7 of the hermetic rotary compressor of the present invention. It is a longitudinal cross-sectional view which shows Embodiment 8 of the sealed rotary compressor of this invention. FIG. 10 is a longitudinal sectional view showing a structural example of the lubricating oil return mechanism in FIG. 9.

  Embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view showing Embodiment 1 of a hermetic rotary compressor of the present invention.

 As shown in FIG. 1, the hermetic rotary compressor 1, the condenser 152, the expansion device 153, and the evaporator 154 constitute a refrigeration cycle apparatus R by communicating in a cycle. The refrigeration cycle apparatus R uses an HFC refrigerant, an HC (hydrocarbon) refrigerant, or a carbon dioxide refrigerant as a refrigerant.

 A hermetic rotary compressor 1 shown in FIG. 1 has a hermetic container 2 and is a rotary compressor in which the hermetic container 2 is filled with a low-pressure refrigerant gas. An electric motor unit 3 and a compression mechanism unit 4 are arranged inside the hermetic container 2, and the electric motor unit 3 is arranged on the upper part of the compression mechanism unit 4. In the hermetic rotary compressor 1, the lubricating oil 99 is stored in the bottom 2 </ b> A of the hermetic container 2. The refrigerant gas is introduced into the upper space in the sealed space 2 from the suction pipe 9B of the refrigeration cycle apparatus R, and the cylinder of the cylinder 8 of the compression mechanism unit 4 from the upper space in the sealed container 2 through the external suction pipe 9A. The air is sucked into the chamber 8a.

 As shown in FIG. 1, the electric motor unit 3 has a rotating shaft 5 along the Z direction. The electric motor unit 3 includes a rotor 3a and a stator 3b, and may be a permanent magnet synchronous motor driven by an inverter, an AC motor, or an AC motor driven by a commercial power source.

 The compression mechanism unit 4 includes a main bearing 6, a sub bearing 7, and a cylinder 8. The rotating shaft 5 is inserted into the shaft through hole 6B of the main bearing 6 and the shaft through hole 7B of the sub bearing 7, and is rotatably supported by the main bearing 6 and the sub bearing 7. The main bearing 6 is disposed above the sub bearing 7, and the cylinder 8 is disposed between the main bearing 6 and the sub bearing 7. An oil supply path 11 is formed in the rotary shaft 5 along the Z direction.

 2 shows the cylinder chamber 9, the roller 10, and the eccentric portion 5A of the rotating shaft 5. FIG. 2A is a plan view of these elements, and FIG. 2B is a plan view of FIG. It is sectional drawing in the AA in FIG.

 As shown in FIGS. 1 and 2, the cylinder 8 has a cylinder chamber 9, and a cylindrical roller 10 is disposed in the cylinder chamber 9 as shown in FIG. . The cylinder 8 has a suction port 8A and a discharge port 8B. The cylinder 8 is provided with a vane groove 11M, and a vane 12 is disposed in the vane groove 11M. The tip of the vane 12 is always pressed against the outer peripheral surface of the roller 10 by a spring 14. The cylinder chamber 9 is divided by the outer peripheral surface of the vane 12 and the roller 10 and the inner peripheral surface of the cylinder 8. The suction port 8A side divided by the vane 12 is a refrigerant gas suction chamber 9P containing lubricating oil, and the discharge port 8B side divided by the vane 12 is a refrigerant gas compression chamber 9R containing lubricating oil. An eccentric portion 5 </ b> A is formed on the rotating shaft 5. The inner peripheral surface of the roller 10 is fitted to the outer peripheral surface of the eccentric portion 5 </ b> A of the rotating shaft 5.

 As shown in FIGS. 1 and 2B, the spring 14 is housed in a vane back chamber 13, and the vane chamber 13 has a function of a lubricating oil reservoir. The vane 12 shown in FIG. 1 slides in the vane groove 11M in the X direction (radial direction of the sealed container 2) while sliding on the outer peripheral surface of the roller 10 according to the rotation of the eccentric portion 5A of the rotating shaft 5 and the roller 10. It is designed to reciprocate along. The X direction and the Z direction are orthogonal to each other.

 As shown in FIG. 1, the suction pipe 9A connects the upper space of the sealed container 2 and the inside of the cylinder chamber 9 through the suction port 8A of the cylinder 8 shown in FIG. The suction pipe 9 </ b> A is disposed outside the sealed container 2. A suction pipe 9 </ b> B is connected to the upper end of the sealed container 2.

 The oil separator 15 shown in FIG. 1 is connected to the discharge port 8B side of the cylinder chamber 9 shown in FIG. A bottom 15A of the oil separator 15 shown in FIG. 1 is connected to the bottom 2A of the sealed container 2 via an oil return passage 17. The oil separator 15 is a separator that separates refrigerant gas and lubricating oil. The oil separator 15 is attached to the sealed container 2, and the bottom portion 15 </ b> A of the oil separator 15 is located higher than the bottom portion 2 </ b> A of the sealed container 2.

 The discharge pipe 16 shown in FIG. 1 has a substantially L shape, and the opening end portion 16 </ b> A opens upward at a position that is approximately 1/3 of the height inside the oil separator 15. Lubricating oil 99 is accommodated in the bottom 2 </ b> A of the sealed container 2 and the bottom 15 </ b> A of the oil separator 15. The level of the lubricating oil 99 in the bottom 2 </ b> A of the sealed container 2 reaches the upper end portion of the main bearing 6, but does not reach the motor unit 3.

 The oil return passage 17 is formed in a step shape, the opening one end 17A is opened to the bottom 15A of the oil separator 15, and the opening other end 17B is opened to the bottom 2A of the sealed container 2. An oil return valve 22 is provided in the middle of the oil return passage 17.

 As shown in FIG. 1, the oil supply passage 6 </ b> A is formed around the shaft through hole 6 </ b> B of the main bearing 6. Similarly, the oil supply passage 7 </ b> A is formed around the shaft through hole 7 </ b> B of the auxiliary bearing 7. The oil supply passages 6 and 7A are both ring-shaped and have an L-shaped longitudinal section. The oil supply paths 6 and 7A are connected to the oil supply path 11.

 As shown in FIG. 1, a positive displacement oil pump device 100 is provided at the lower end of the rotating shaft 5. The positive displacement oil pump device 100 can employ, for example, a trochoid type, although not shown. The positive displacement oil pump device 100 is provided with a suction port (not shown) immersed in the lubricating oil 99, and the lubricating oil discharged from the positive displacement oil pump device 100 is applied to the sliding portion of the compression mechanism section 4. It comes to supply. That is, the positive displacement oil pump device 100 sucks the lubricating oil 99 in the lubricating oil pool in the bottom 2 </ b> A of the sealed container 2. Then, the positive displacement oil pump device 100 shown in FIG. 1 passes through the oil supply passage 11 and the oil supply holes 11P and 11Q provided in the rotary shaft 5 shown in FIG. 2 (B) and the oil supply passages 6A and 7A shown in FIG. 2B, the sliding part 101 between the upper and lower main bearings 6, the auxiliary bearing 7, and the rotating shaft 5, the sliding part 102 between the roller 10 and the cylinder 8, and the roller 10 and rotation. The shaft 5 is supplied to the sliding portion 103 with the eccentric portion 5A. As described above, the positive displacement oil pump device 100 supplies the lubricating oil 99 to the sliding portions 101, 102, and 103, thereby positively supplying the lubricating oil 99 having an appropriate pressure to the sliding portions around the rotating shaft 5. it can. As a result, the lubricating oil is supplied also into the cylinder chamber 9 in the same manner as the rotary compressor in which the inside of the normal hermetic container has a discharge pressure, thereby improving the sealing performance of the compression chamber and suppressing the performance deterioration. it can. For this reason, the sliding part is sealed to prevent leakage of the refrigerant gas.

 As shown in FIG. 1, a lubricant return mechanism 50 is provided in the main bearing 6. The lubricant return mechanism 50 corresponds to the pressure control mechanism in the embodiment of the present invention. The lubricating oil return mechanism 50 is provided in communication with the oil supply path 11 of the rotating shaft 5 and is introduced into the sliding portions 102 and 103 in the cylinder chamber 9 as described above in the lubricating oil supplied. In addition, excess lubricating oil 99 other than leaking to the bottom portion 2A of the sealed container 2 from the clearance between the rotary shaft 5, the upper and lower main bearings 6 and the sub-bearing 7 or the like is removed by the lubricating oil return mechanism 50 by the bottom 2A of the sealed container 2. It is supposed to be returned to. Since the lubricating oil return mechanism 50 is disposed in the return passage of the lubricating oil into the hermetic container 2, even when the lubricating oil is excessively supplied by the positive displacement oil pump device 100, the pressure in the oil supply path 11 is abnormal. There is no increase, and damage to the positive displacement oil pump device 100 and an increase in sliding loss of the sliding portion can be prevented.

 FIG. 3 is a cross-sectional view showing a structural example of the lubricating oil return mechanism 50.

 As shown in FIG. 3, the lubricating oil return mechanism 50 controls the pressure of the lubricating oil in the return passage. The lubricating oil return mechanism 50 has a discharge path 55, a cylindrical hole 56, a piston 57, a lateral hole 58, and a spring 59. The discharge path 55 and the cylindrical hole 56 are formed to be connected in the main bearing 6, and a piston 57 and a spring 59 are arranged in the middle of the cylindrical hole 56. The horizontal hole 58 is connected to the middle of the cylindrical hole 56, and the cylindrical hole 56 communicates with the inside of the sealed container 2 through the horizontal hole 58. The cylindrical hole 56 is connected to the oil supply path 11 via the oil supply path 11R and the oil supply path 6A shown in FIG.

 As shown in FIG. 3, one end 57 </ b> A of the piston 57 faces the oil supply path 11, and the other end 57 </ b> B of the piston 57 faces the discharge path 55. Thereby, the discharge pressure of the discharge chamber 54 is introduced into the other end portion 57 </ b> B of the piston 57 via the discharge passage 55. A discharge pipe 16 opening end 16B is connected to the discharge chamber 54. As described above, in FIG. 3, the oil supply path 11 and the one end 57A side of the piston 57 are released to the suction pressure through the cylindrical hole 56 and the lateral hole 58, and the discharge pressure of the discharge chamber 54 is on the other end 57B side of the piston 57. Has been introduced.

 Next, an operation example of the above-described hermetic rotary compressor 1 will be described.

 During operation of the hermetic rotary compressor 1, the low-pressure refrigerant gas in the hermetic container 2 is compressed by the roller 10 that rotates eccentrically in the cylinder 8 to become a high-pressure refrigerant gas containing the lubricating oil 99. The oil is ejected from the open end 16A toward the upper side of the oil separator 15. In the oil separator 15, the lubricating oil 99 is separated from the high-pressure gas containing the lubricating oil 99 by the ejection of the high-pressure refrigerant gas containing the lubricating oil 99, and the lubricating oil 99 is stored in the bottom 15 </ b> A of the oil separator 15. Is done.

 On the other hand, the oil separator 15 is filled with high-pressure refrigerant gas and becomes high-pressure, and the lubricating oil 99 stored in the bottom portion 15A is pressed by the pressure of the high-pressure refrigerant gas, and the oil is generated by the differential pressure. The return passage 17 is returned to the bottom 2A of the sealed container 2 from the opening one end 17A. The oil return valve 22 is opened and closed according to the oil level of the bottom 15A of the oil separator 15 so that the high-pressure refrigerant gas in the oil separator is not returned to the bottom 2A of the hermetic container 2.

 Here, the operation of the lubricating oil return mechanism 50 described above will be described.

 In FIG. 3, when the pressure in the oil supply passage 11 is low, the arrow 57 in the left direction in FIG. 3 is caused by the pressure difference between the discharge pressure in the discharge chamber 54 and the pressure in the oil supply passage 11 and the elastic force of the spring 59. The lateral hole 58 is blocked by the piston 57. Lubricating oil is supplied to the oil supply passage 11 from the positive displacement oil supply pump device 100, and the pressure in the oil supply passage 11 gradually increases. When the pressure in the oil supply path 11 becomes larger than the total force of the discharge pressure and the elastic force of the spring 59, the piston 57 is pushed in the X1 direction against the force of the spring 59, and the oil supply path 11 is in the horizontal hole of the cylinder 6. 58 communicates. Lubricating oil is discharged from the oil supply path 11 into the sealed container 2 through the lateral hole 58. Thus, when the pressure in the oil supply path 11 exceeds the discharge pressure, the lubricating oil is returned into the sealed container 2, so that the lubricating oil supplied from the oil supply path 11 to each sliding portion is also a pressure close to the discharge pressure. The lubricating oil will be supplied. Accordingly, the lubricating oil is easily supplied into the cylinder chamber 9 as well as the rotary compressor in which the inside of the normal hermetic container 11 has a discharge pressure, and the sealing performance of the compression chamber is improved and the deterioration in performance is suppressed. Is done. In addition, since the lubricating oil return mechanism 50 is provided, the pressure in the oil supply path 11 does not rise abnormally even when the oil supply by the positive displacement oil pump device 100 is excessive, and damage or loss of the positive displacement oil pump device 100 is prevented. Can prevent the increase.

 On the other hand, when the pressure in the oil supply path 11 decreases, the piston 57 is pushed back in the X2 direction by the force of the spring 59, and the lateral hole 58 is closed by the piston 57. Thereby, the lubricating oil is not discharged into the sealed container 2 from the oil supply path 11 through the lateral hole 58.

 As described above, the lubricating oil 99 having a discharge pressure is supplied to each sliding portion 101, 102, 103 in an appropriate amount by the discharge pressure, and a gap between the roller 10 and the main bearing 6 and the sub-bearing 7 is placed in the cylinder chamber 9. Since the lubricating oil 99 is supplied through, the same lubrication and sealing of the compression chamber as the rotary compressor in which the inside of the hermetic container 2 becomes the discharge pressure can be performed, so that it is possible to prevent performance degradation and reliability degradation. . Moreover, since the lubricating oil return mechanism 50 maintains the pressure of the oil supply path 11 appropriately, a loss does not increase due to an excessive increase in pressure, and an excessive load is not applied to the positive displacement oil pump device 100.

 When the hermetic rotary compressor 1 is stopped, the pressure in the refrigeration cycle apparatus R and the hermetic rotary compressor 1 is balanced, and the oil level of the lubricating oil 99 in the hermetic container 2 and the oil separator 15 are balanced. The lubricating oil 99 has the same oil level.

 Next, another embodiment of the hermetic rotary compressor of the present invention will be described.

 In the embodiment of the present invention described below, the same reference numerals are given to the substantially same portions as those of the first embodiment of the present invention shown in FIGS.

(Embodiment 2)
FIG. 4A is a longitudinal sectional view showing Embodiment 2 of the present invention.

 The lubricating oil return mechanism 50 shown in FIG. 4A corresponds to a pressure control mechanism. The lubricant return mechanism 50 is provided in the main bearing 6 and has a path 55A, a cylindrical hole 56, a piston 57, a lateral hole 58, and a spring 59. The path 55 </ b> A and the cylindrical hole 56 are connected to each other in the main bearing 6, and a piston 57 and a spring 59 are arranged in the middle of the cylindrical hole 57. The horizontal hole 58 is connected to the middle of the cylindrical hole 56, and the cylindrical hole 56 communicates with the inside of the sealed container 2 through the horizontal hole 58. The cylindrical hole 56 is connected to the oil supply path 11 via the oil supply path 11R and the oil supply path 6A shown in FIG.

 As shown in FIG. 4A, one end 57A of the piston 57 faces the oil supply path 11 side. The other end 57B of the piston 57 is opened into the sealed container 2 (suction pressure) through the passage 55A. An opening end 16B of the discharge pipe 16 is connected to the discharge chamber 54. 4A, the oil supply path 11 and the one end 57A side of the piston 57 can be released to the suction pressure through the cylindrical hole 56 and the lateral hole 58, and the other end 57B side of the piston 57 is sucked. Open to pressure.

 In FIG. 4A, when the pressure in the oil supply path 11 increases, the piston 57 overcomes the force of the spring 59 and is pushed in the X1 direction, and the oil supply path 11 communicates with the lateral hole 58 of the cylinder 6. As a result, the lubricating oil is discharged from the oil supply path 11 into the sealed container 2 through the lateral hole 58.

 On the other hand, when the pressure in the oil supply path 11 decreases, the piston 57 is pushed back in the X2 direction by the force of the spring 59, and the lateral hole 58 is closed by the piston 57. As a result, the lubricating oil is not discharged from the oil supply path 11 into the sealed container 2 through the lateral hole 58. Depending on the set value of the pressing force of the spring 59, the pressure in the oil supply path 11 is generally maintained at an appropriate intermediate pressure between the suction pressure and the discharge pressure. Thereby, the effect when the inside of the oil supply path 11 becomes high is the same as in the case of the first embodiment, but the oil supply pressure of the positive displacement oil pump device 100 becomes smaller than the discharge force. The load applied to the fuel is reduced, the power for refueling is reduced, and the efficiency is improved.

(Embodiment 3)
FIG. 4B is a longitudinal sectional view showing Embodiment 3 of the present invention.

 The lubricating oil return mechanism 50 shown in FIG. 4B corresponds to a pressure control mechanism. The lubricant return mechanism 50 is provided in the main bearing 6 and has a discharge path 55, a cylindrical hole 56, a piston 57, a lateral hole 58, and a spring 59. The discharge path 55 and the cylindrical hole 56 are formed to be connected in the main bearing 6, and a piston 57 and a spring 59 are arranged in the middle of the cylindrical hole 56. However, unlike the case of the first embodiment shown in FIG. 3, the arrangement order of the piston 57 and the spring 59 is reversed. That is, the spring 59 is disposed on the oil supply path 11 side, and the piston 57 is disposed on the discharge path 55 side. The spring 59 urges the piston 57 in the X1 direction, which is the right direction in FIG. The cylindrical hole 56 can communicate with the sealed container 2 through the lateral hole 58, and the oil supply path 11 is opened to the pressure (suction pressure) in the sealed container 2. The cylindrical hole 56 is connected to the oil supply path 11 via the oil supply path 11R and the oil supply path 6A shown in FIG.

 As shown in FIG. 4B, one end 57A of the piston 57 faces the oil supply path 11 side, and the other end 57B of the piston 57 faces the discharge path 55 side. Thereby, the discharge pressure of the discharge chamber 54 is introduced into the other end portion 57 </ b> B of the piston 57 via the discharge passage 55. An opening end 16B of the discharge pipe 16 is connected to the discharge chamber 54. 4B, the oil supply path 11 and the one end 57A side of the piston 57 are opened to the suction pressure through the cylindrical hole 56 and the lateral hole 58, and the discharge chamber 54 is provided on the other end 57B side of the piston 57. The discharge pressure is introduced. Since the piston 57 is pushed in the X1 direction by the force of the spring 59, it communicates with the sealed container 2 through the oil supply path 11 and the lateral hole 58, and the force generated by the pressure in the oil supply path 11 and the force of the spring 59 are When the total force becomes larger than the force due to the discharge pressure, the piston 57 is pushed in the X1 direction, the oil supply path 11 connects the cylindrical hole 56 and the lateral hole 58, and the lubricating oil is discharged into the sealed container 2. .

 Accordingly, a bias force can be applied by the force of the spring 59, and the oil supply path 11 is maintained at a pressure lower than the discharge pressure by a certain value. Accordingly, the lubricating oil can be returned into the closed container 2 on the low pressure side at a pressure lower than the discharge pressure by a certain value. The effect when the pressure in the oil supply path becomes high is the same as in the case of the first embodiment. However, as in the case of the second embodiment, the oil supply pressure of the positive displacement oil pump device 100 is smaller than the discharge force. The load applied to the type oil pump device 100 is reduced, the power for oil supply is reduced, and the efficiency is improved.

 In the embodiment of FIGS. 4 (A) and 4 (B), since the lubricating oil is supplied to the sliding portion, the same lubrication and compression chamber as in the rotary type compressor in which the inside of the hermetic container has a discharge pressure is used. Since sealing can be performed, it is possible to prevent deterioration in performance and reliability. Moreover, since the oil supply pressure of the positive displacement oil pump device is lower than the discharge pressure by a certain value, the load applied to the positive displacement oil pump device is reduced, the power for oil supply is reduced, and the efficiency is improved.

(Embodiment 4)
FIG. 5 is a longitudinal sectional view showing Embodiment 4 of the hermetic rotary compressor of the present invention.

 The sealed rotary compressor 1A according to the fourth embodiment shown in FIG. 5 has almost the same structure as the sealed rotary compressor 1 according to the first embodiment shown in FIG. 1, but the vane back chamber 13 is a cylinder. 8 is formed on the back side of the vane 12, and the oil supply passage 11 is communicated with the vane back chamber 13 by an oil supply passage 14T. Thereby, since the lubricating oil 99 can be reliably supplied to the sliding portion of the vane 12 through the oil supply paths 11 and 14T, seizure of the vane 12 and an increase in sliding loss due to insufficient lubricating oil can be prevented.

(Embodiment 5)
FIG. 6 is a longitudinal sectional view showing Embodiment 5 of the hermetic rotary compressor of the present invention.

 The sealed rotary compressor 1B according to the fifth embodiment shown in FIG. 6 is different from the sealed rotary compressor 1 according to the first embodiment shown in FIG. 1 and the sealed rotary compressor 1A according to the fourth embodiment shown in FIG. The compression mechanism unit 4 is located at the upper part of the electric motor unit 3. The rotating shaft 5 of the electric motor unit 3 passes through the electric motor unit 3 and extends to the lower part of the electric motor unit 3, and a positive displacement oil pump device 100 is provided at the lower end of the rotating shaft 5.

A suction port 9 </ b> C of the cylinder 8 is opened in the sealed container 2. Note that the suction port 9C of the cylinder 8 avoids the vicinity of the suction pipe 9B of the sealed container 2 and prevents the liquid refrigerant mixed in with the suction gas from entering the sealed container 2 from being sucked. According to the above configuration, it is not necessary to provide the suction passage 9A outside the sealed container 2 as in the first embodiment shown in FIG. 1 and the fourth embodiment shown in FIG. 5 in order to guide the suction gas. Further, since it is not necessary to provide the suction passage 9A outside the sealed container 2, the suction gas is not drawn out and overheated, and the performance is not deteriorated due to overheating of the suction gas. Thus, according to the said structure, since the suction port of the refrigerant gas of a cylinder becomes above a lubricating oil surface, a suction port can be directly open | released and provided in a sealed container. Therefore, it is not necessary to provide the piping outside the sealed container. Further, since the suction gas is not drawn to the outside, it is not heated by the outside air, and the performance is not deteriorated due to the heating of the suction gas.

  In this embodiment, as in the sixth embodiment described below, an oil separator is provided in the discharge passage outside the compressor, and the oil return passage from the oil separator serves as an oil supply for the compression mechanism portion of the compressor. You may make it communicate with an oil supply path | route via a path | route.

(Embodiment 6)
FIG. 7 is a longitudinal sectional view showing Embodiment 6 of the hermetic rotary compressor of the present invention.

 In the hermetic rotary compressor 1C of the sixth embodiment shown in FIG. 7, the oil separator 15 is provided in the discharge passage 16 outside the compressor 1C, and the oil return passage 17 from the oil separator 15 is connected to the compressor 1C. Is connected to the oil supply path 11 via the oil supply path 14T of the compression mechanism section 4 of the compressor.

 In general, in a compressor that guides discharge gas from a cylinder chamber directly to the outside of a sealed container, lubricating oil contained in the discharge gas is separated and returned to an oil reservoir in the sealed container. This is because if the oil separator is not provided, the amount of lubricating oil circulating in the refrigeration cycle device will increase, resulting in performance degradation due to heat exchange inhibition or the like, or the oil level of the lubricating oil pool in the sealed container This is because there is a shortage of oil and a shortage of refueling occurs. In a compressor in which the suction gas is guided into the sealed container, when the lubricating oil separated by the oil separator is returned to the lubricating oil reservoir in the sealed container, oil separation is performed to prevent the discharged gas from returning. It is necessary to provide and control an oil return valve that operates by detecting the oil level in the vessel.

 In contrast, as shown in FIG. 7, the oil return passage 17 from the oil separator 15 is configured to communicate with the oil supply passage 11 via the oil supply passage 14T of the compression mechanism section 4 of the compressor 1C. Thus, the oil return passage 17 returns the lubricating oil 99 to the oil supply passage 14T near the discharge pressure, and there is no need to provide an oil return valve. The oil separator is desirably provided at such a height that the separated lubricating oil is returned to the oil supply path by the action of gravity.

 Further, when the oil supply path 11 is set to a pressure lower than the discharge pressure as in the second embodiment of the present invention shown in FIG. 4A and the third embodiment of the present invention shown in FIG. The lubricating oil separated by the separator can be returned naturally by the pressure difference, but in this case, an oil return valve that operates by detecting the oil level in the oil separator is controlled so that the discharge gas does not return. There is a need to.

 In Embodiment 6 of FIG. 7, since the lubricating oil is returned to the path near the discharge pressure, the energy of the high-pressure lubricating oil is not returned to the suction pressure and discharged unnecessarily.

(Embodiment 7)
FIG. 8 is a longitudinal sectional view showing Embodiment 7 of the hermetic rotary compressor of the present invention.

 In the hermetic rotary compressor 1D of the seventh embodiment shown in FIG. 8, a check valve 129 is additionally provided with respect to the oil return passage 17 in the hermetic rotary compressor 1C of the sixth embodiment shown in FIG. It has been. The check valve 129 is provided to prevent the lubricating oil 99 from entering the oil separator 15 through the oil return passages 17 from the oil supply passages 11 and 14T of the compressor. Thereby, even when the rotational speed of the compressor is high and the oil supply amount of the positive displacement oil pump device 100 is large, the supplied lubricating oil 99 enters the oil separator 15 side and the oil separator 15 becomes full and separates. Prevent loss of ability.

(Embodiment 8)
FIG. 9 is a longitudinal sectional view showing Embodiment 8 of the hermetic rotary compressor of the present invention.

 The hermetic rotary compressor 1E of the seventh embodiment shown in FIG. 9 has basically the same structure as the hermetic rotary compressor 1 of the seventh embodiment shown in FIG. The difference is that oil supply pump devices 100P and 100R are provided. In this example, a two-stage positive displacement oil pump device is shown, but the number of stages is not limited. The first stage (previous stage) positive displacement oil pump apparatus 100P and the second stage (final stage) positive displacement oil pump apparatus 100R can employ, for example, a trochoidal type.

 When the first-stage positive displacement oil pump device 100P sucks the lubricating oil 99 in the hermetic container 2, the sucked lubricating oil 99 is discharged to the next-stage positive displacement oil pump device 100R via the oil reservoir 124. However, the oil reservoir 124 is provided with a lower lubricating oil return mechanism 50 as a pressure control mechanism. The oil sump 124 communicates with the second-stage positive displacement oil pump device 100R, and the second-stage positive displacement oil pump device 100R communicates with another upper lubricating oil return mechanism 50 through the oil supply path 11.

 Thus, since the multistage positive displacement oil pump devices 100P and 100R are provided, the lubricating oil 99 is maintained so as to keep the oil supply path 11 at a predetermined high pressure even when the difference between the suction pressure and the discharge pressure of the compressor is large. Can be pressurized. The discharge pressure of the lubricating oil 99 in the last-stage positive displacement oil pump device 100R is changed according to the discharge pressure of the hermetic rotary compressor 1E, and the discharge pressure of the lubricating oil 99 in the previous positive displacement oil pump device 100P is Each pressure control mechanism 50 adjusts the pressure so as to obtain a predetermined pressure.

 For this reason, an appropriate amount of oil is always supplied to each sliding portion, and the lubricating oil is supplied into the cylinder chamber 9 through the gap between the roller 10 and the main bearing 6 and the auxiliary bearing 7. The same lubrication and sealing of the compression chamber as those of the rotary compressor in which the inside becomes the discharge pressure is performed, and the performance and reliability can be prevented from being lowered. Further, the lubricating oil return mechanisms 50 and 50 maintain the pressure of the lubricating oil at each stage appropriately, and an excessive increase in pressure does not increase pressure loss or apply an excessive load to the positive displacement oil pump device.

 The two lubricating oil return mechanisms 50 and 50 as the pressure control mechanism shown in FIG. 9 can adopt the structure shown in FIG. 3 or the structure shown in FIGS. 4 (A) and 4 (B). The two lubricant return mechanisms 50, 50 can employ the structure shown in FIG.

 FIG. 10 is a longitudinal sectional view showing another structure of the lubricating oil return mechanism 50. The lubricating oil return mechanism 50 has a path 55A, a cylindrical hole 56, a piston 57, a lateral hole 58, and a spring 59. The path 55 </ b> A and the cylindrical hole 56 are connected to each other, and a piston 57 and a spring 59 are disposed in the middle of the cylindrical hole 57. The horizontal hole 58 is connected to the middle of the cylindrical hole 56, and the cylindrical hole 56 can communicate with the sealed container 2 through the horizontal hole 58, and the path 55 </ b> A also communicates with the sealed container 2 (suction pressure). The cylindrical hole 56 is connected to the oil sump 124 of FIG.

 One end portion 57A of the piston 57 in FIG. 10 faces the oil supply passage 11 through the oil reservoir 124 in FIG. 9, and the one end portion 57A side of the oil supply passage 11 and the piston 57 passes through the cylindrical hole 56 and the lateral hole 58 in the sealed container 2. (Suction pressure) can be released. The other end 57B of the piston 57 faces the inside of the sealed container 2 through the path 55A, and suction pressure is introduced.

 In FIG. 10, when the pressure in the oil supply path 11 increases, the piston 57 overcomes the force of the spring 59 and is pushed in the X1 direction, and the oil supply path 11 communicates with the lateral hole 58 of the cylinder 6. As a result, the lubricating oil is discharged from the oil supply path 11 into the sealed container 2 through the lateral hole 58.

 On the other hand, when the pressure in the oil supply path 11 decreases, the piston 57 is pushed back in the X2 direction by the force of the spring 59, and the lateral hole 58 is closed by the piston 57. Thereby, the oil supply path 11 is kept at a predetermined value by setting the pressing force of the spring 59.

 The first-stage positive displacement oil pump device 100P shown in FIG. 9 is set to a predetermined pressure. For example, in the second-stage positive displacement oil pump device 100R, when the discharge pressure of the first-stage positive displacement oil pump device 100P is set to the suction pressure of the compressor + 5 MPa, the discharge pressure of the compressor is 10 MPa. Then, the positive displacement oil pump device 100R in the second stage may be pressurized at 5 MPa. On the other hand, when the discharge pressure of the compressor becomes 3 MPa, the pressure in the oil supply passage 11 is maintained in the vicinity of 3 MPa by the lubricating oil return mechanism 50. Therefore, in the second-stage positive displacement oil pump device 100R, 5 MPa To about 3 MPa.

 When a multistage positive displacement oil pump device and a lubricating oil return mechanism, which is a pressure control mechanism, are provided, the positive displacement oil pump device is provided in a plurality of stages. A pressure control mechanism for controlling the pressure is provided, and the discharge side of the positive displacement oil pump device at the final stage is connected to the oil supply path of the compressor, and the discharge pressure of the lubricating oil at the positive displacement oil pump device at the final stage is hermetically sealed The pressure control mechanism adjusts the pressure such that the discharge pressure of the rotary compressor is changed according to the discharge pressure of the rotary compressor and the discharge pressure of the lubricating oil in the former positive displacement oil supply pump device becomes a predetermined pressure.

 As described above, even if the difference between the discharge pressure and the suction pressure of the compressor is large and the single-stage positive displacement oil pump device cannot pressurize the lubricating oil to a predetermined pressure, the positive displacement oil pump device can be divided into multiple stages or By using multiple stages, the lubricating oil can be pressurized to a predetermined high pressure. In addition, since each positive displacement oil pump device is provided with a lubricating oil return mechanism 50, the pressure in the oil supply path does not rise abnormally even in the case of excessive oil supply, and damage to the positive displacement oil pump device. Increase in sliding loss can be prevented. Even if the discharge pressure changes depending on the operating conditions of the compressor, the pressure in the oil supply path is always kept optimal following the discharge pressure, the optimal lubricating oil is supplied into the cylinder 8, and the sealing performance of the compression chamber is improved. And the compressor performance is improved.

  The present invention is not limited to the above embodiment. Furthermore, various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the embodiments of the present invention. For example, you may delete some components from all the components shown by embodiment of this invention. Furthermore, you may combine the component covering different embodiment suitably.

DESCRIPTION OF SYMBOLS 1 ... Sealed rotary compressor, 2 ... Sealed container, 2A ... Bottom part of sealed container, 3 ... Electric motor part, 5 ... Rotating shaft, 5A ... Eccentric part of rotating shaft, 4 ... Compression mechanism part, 6 ... Main bearing, 7 ... Sub bearing, 8 ... Cylinder, 9 ... Cylinder chamber, 9A ... Suction pipe, 10 ... Roller, 11 ... Oil supply passage, 11M ... Vane groove, 12 ... Vane, 13 ... Vane chamber, 14 ... Spring, 15 ... Oil separation 15A ... bottom of oil separator 16 ... discharge pipe 17 ... oil return passage 22 ... oil return valve 50 ... lubricating oil return mechanism 55 ... discharge path 56 ... cylindrical hole 57 ... piston 58 ... Horizontal hole, 59 ... spring, 99 ... lubricating oil, 100 ... positive displacement oil pump device, R ... refrigeration cycle device,

Claims (7)

A sealed rotary type in which a motor unit and a compression mechanism unit driven by the motor unit are housed in a sealed container storing lubricating oil at the bottom, and refrigerant is sucked into the compression mechanism unit through a space in the sealed container In the compressor,
A positive displacement oil pump device is provided by immersing the suction port in the lubricant oil, the lubricant oil discharged from the positive displacement oil pump device is supplied to the sliding portion of the compression mechanism portion, and the lubricant oil A hermetic rotary compressor characterized in that a pressure control mechanism for controlling the pressure of lubricating oil in the return passage is provided in a return passage to the hermetic container.   The pressure control mechanism is configured to return the lubricating oil into the sealed container when a pressure of the lubricating oil in the oil supply path exceeds a discharge pressure of the refrigerant. The hermetic rotary compressor described in 1.   The pressure control mechanism is configured to seal the lubricating oil when the pressure of the lubricating oil in the oil supply path becomes a predetermined pressure between the refrigerant discharge pressure and the suction pressure or a pressure lower than the discharge pressure by a predetermined value. The hermetic rotary compressor according to claim 1, wherein the hermetic rotary compressor is configured to be returned into the container.   2. The hermetic rotary compressor according to claim 1, wherein the compression mechanism unit is positioned above the electric motor unit.   The positive displacement oil pump device is provided in a plurality of stages, and the pressure control mechanism for controlling the pressure of the lubricating oil is provided on the discharge side of the positive displacement oil pump device in each stage. The hermetic rotary compressor described in 1. The positive displacement oil pump device is provided in a plurality of stages, the pressure control mechanism for controlling the pressure of the lubricating oil is provided on the discharge side of the positive displacement oil pump device of each stage, and the positive displacement oil supply in the final stage. The discharge side of the pump device communicates with the oil supply path of the compressor,
The discharge pressure of the lubricating oil in the positive displacement oil supply pump device in the final stage is changed according to the discharge pressure of the compression mechanism, and the discharge pressure of the lubricating oil in the positive displacement oil supply pump device in the previous stage is a predetermined pressure. The hermetic rotary compressor according to claim 1, wherein the pressure control mechanism is configured to adjust pressure.   A refrigeration cycle apparatus comprising the hermetic rotary compressor according to claim 1, a condenser, an expansion device, and an evaporator.

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