JP2020002906A - Compressor - Google Patents

Abstract

To maintain supply of lubrication oil to each bearing part and an oil circulation ratio in proper states.SOLUTION: A compressor 1 includes: a rotary shaft 20 extending along an axis O1; a bearing 30 rotatably supporting the rotary shaft 20; a drive part 50 which rotationally drives the rotary shaft 20; a compressor body 60 which is rotated by the rotary shaft 20 to compress a fluid; a casing 10 which houses the rotary shaft 20, the drive part 50, and the compressor body 60 and stores lubrication oil for lubricating the bearing part 30 therein; and multiple suction pipes 80 which supply the fluid to be compressed to an interior of the casing 10. The suction pipes 80 have: a first suction pipe 81 connected to the casing 10; and a second suction pipe 82 which is connected to the casing 10 at a position such that the second suction pipe 82 contacts the lubrication oil relatively easily compared to a connection position of the first suction pipe 81 with the casing 10.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor.

  2. Description of the Related Art As a compressor, a compressor in which a rotating shaft, an electric motor that rotates the rotating shaft, and a compression mechanism that is driven by the rotating force of the rotating shaft and compresses a working fluid are housed in a sealed casing is known. This type of compressor is connected to a refrigerant circuit of, for example, a refrigeration apparatus, and is used to compress refrigerant gas in the refrigerant circuit. In such a compressor, a scroll compressor or a rotary compressor is employed as a compression mechanism.

  For example, Patent Literature 1 discloses a compressor in which refrigerant gas is supplied from two suction pipes into a closed container that is a casing. The compressor described in Patent Document 1 has a scroll compressor as a compression mechanism. An accumulator chamber for storing lubricating oil is formed at the bottom in the closed container. In this compressor, a compression chamber formed by an orbiting scroll and a fixed scroll is provided on an accumulator chamber. In this compressor, the refrigerant gas is supplied into the closed container from a suction pipe connected to a radial outside of the compression chamber and a suction pipe connected to the accumulator chamber.

Japanese Patent No. 2568711

  By the way, in a compressor having a closed casing, an appropriate amount of lubricating oil is applied to a bearing portion that rotatably supports a rotating shaft in order to ensure mechanical lubrication in a compressor body that is a compression mechanism. Need to supply. At this time, a part of the lubricating oil supplied to each bearing part scatters from the sliding part or the like, and the lubricating oil is contained in the refrigerant gas in the casing. As an index indicating the state, there is an OCR (Oil Circulation Ratio) indicating a ratio of lubricating oil to a refrigerant gas in the casing. A high OCR indicates that the lubricating oil contained in the refrigerant gas is large, and a low OCR indicates that the lubricating oil is low. Generally, the OCR tends to increase as the amount of oil supplied to the bearing increases.

  Even if the compressor body is operated at a low speed, if a sufficient amount of lubricating oil is supplied to the bearings, the amount of oil supplied to each bearing increases as the rotation speed increases. Therefore, during high-speed operation, the supply amount of the lubricating oil to the bearing portion becomes excessive, and the OCR may become extremely high. As a result, the lubricating oil inside the compressor may be depleted or the compression performance may be reduced during high-speed operation.

  Conversely, if the OCR is set to be low during high-speed operation, the supply of lubricating oil may be insufficient during low-speed operation, even if reliability and performance during high-speed operation can be ensured. As a result, at the time of low-speed operation, not only the performance of the bearing portion cannot be ensured, but also the OCR becomes too low, so that the sealing performance in the compressor body may be reduced and the leakage loss may increase. Therefore, it is desired to maintain the lubricating oil supply state in an appropriate state regardless of the operating state of the compressor body.

  The present invention has been made to solve the above problems, and has as its object to provide a compressor capable of maintaining a supply state of lubricating oil to each bearing portion and an OCR in an appropriate state. .

  The compressor according to the first aspect of the present invention includes a rotating shaft that extends along an axis, a bearing that rotatably supports the rotating shaft, a driving unit that drives the rotating shaft to rotate, and the rotating shaft. A compressor body that compresses a fluid by rotating by a casing, a casing that houses the rotating shaft, the drive unit, and the compressor body, and that stores therein lubricating oil that lubricates the bearing unit; A plurality of suction pipes for supplying fluid before compression to the, the plurality of suction pipes, the first suction pipe connected to the casing, and a connection position of the first suction pipe to the casing, A second suction pipe connected to the casing at a position relatively easily in contact with the lubricating oil.

  According to such a configuration, as compared with the case where only one suction pipe is provided, the flow velocity when flowing into the casing is reduced due to an increase in the flow path area, and the flow rate from each suction pipe is reduced. The effect of the flowing fluid can be suppressed. As a result, it is possible to suppress the fluctuation of the OCR due to the fluid supplied from each suction pipe. Further, the fluid flowing from the second suction pipe contains more lubricating oil before reaching the compressor body than the fluid flowing from the first suction pipe. In other words, the fluid supplied from the first suction pipe and the fluid supplied from the second suction pipe are sent to the compressor main body in different lubricating oil amounts. The ability to supply fluids containing different amounts of lubricating oil facilitates increasing and decreasing the OCR. As a result, it becomes easier to manage the OCR in the casing.

  In the compressor according to the second aspect of the present invention, in the first aspect, the pipe diameter of the second suction pipe may be smaller than the pipe diameter of the first suction pipe.

  According to such a configuration, more fluid flows into the casing from the first suction pipe than from the second suction pipe. Therefore, the supply amount of the fluid containing less lubricating oil is larger than the supply amount of the fluid containing more lubricating oil. By supplying a large amount of fluid containing little lubricating oil, the operating performance of the compressor body during high-speed operation can be stabilized.

  In the compressor according to the third aspect of the present invention, in the first or second aspect, the first suction pipe is located at a position away from an inlet of the compressor body in an axial direction in which the rotation shaft extends. And may be connected to the casing at a position closer to the drive unit than to the compressor body.

  According to such a configuration, even if lubricating oil is contained in the fluid supplied from the first suction pipe into the casing, the lubricating oil is separated from the fluid before reaching the suction port. As a result, a fluid containing less lubricating oil can be supplied to the suction port.

  In the compressor according to a fourth aspect of the present invention, in any one of the first to third aspects, the first suction pipe is arranged about the rotation axis with respect to a suction port of the compressor body. It may be connected to the casing at a radially outer side.

  According to such a configuration, the fluid supplied from the first suction pipe into the casing is supplied to the suction port at a short distance. Therefore, it is possible to suppress the lubricating oil flowing in the casing from being caught in the fluid flowing into the casing from the first suction pipe. As a result, the refrigerant gas containing less lubricating oil can be supplied to the suction port.

  In the compressor according to a fifth aspect of the present invention, in any one of the first to fourth aspects, the casing may include a storage unit in which the lubricating oil is stored, and the storage unit from the storage unit to the bearing unit. A lubricating oil supply path through which lubricating oil is supplied; and a lubricating oil discharge path that sends the lubricating oil used in the bearing section from the bearing section to the storage section. It may be connected to the casing at a position facing at least one of an oil discharge path and the storage section.

  According to such a configuration, the fluid supplied into the casing from the second suction pipe passes through the lubricating oil flowing through the lubricating oil discharge path or the lubricating oil stored in the storage unit, and then flows into the suction port. To reach. Thereby, the amount of lubricating oil contained in the fluid flowing into the casing from the second suction pipe increases. Therefore, a fluid containing a large amount of lubricating oil can be supplied to the suction port.

  In the compressor according to a sixth aspect of the present invention, in the fifth aspect, the casing forms a part of the lubricating oil discharge path and has a guide member that guides the lubricating oil to the storage unit, The second suction pipe may be connected to the casing at a position overlapping the guide member in an axial direction in which the rotation shaft extends.

  According to such a configuration, the fluid flowing into the casing from the second suction pipe passes through the lubricating oil flowing along the guide member. Therefore, the fluid is more likely to come into contact with the lubricating oil. Thereby, a fluid containing more lubricating oil can be supplied to the suction port.

  In the compressor according to the seventh aspect of the present invention, in any one of the first to sixth aspects, the first flow rate adjusting valve capable of adjusting a flow rate of the fluid flowing through the first suction pipe, A second flow control valve capable of adjusting a flow rate of the fluid flowing through a second suction pipe, and at least one of a rotation speed of the rotating shaft and a pressure of the compressor body, the first flow control valve and the A control unit for adjusting the opening degree of the second flow control valve may be provided.

  According to such a configuration, the openings of the first flow control valve and the second flow control valve are controlled in accordance with the rotation speed and the pressure. Thereby, the supply amount of the fluid supplied from the first suction pipe and the second suction pipe can be adjusted according to the operation state of the compressor body.

  In the compressor according to an eighth aspect of the present invention, in the seventh aspect, the control unit is configured to control the first suction pipe when at least one of the rotation speed and the pressure exceeds a predetermined upper limit reference value. The opening of the first flow control valve and the second flow control valve may be adjusted such that the flow rate of the fluid supplied from the second suction pipe is greater than the flow rate of the fluid supplied from the second suction pipe. .

  According to such a configuration, when the compressor main body operates at high speed, the supply amount of the fluid containing a large amount of lubricating oil decreases, and the supply amount of the fluid containing little lubricating oil increases. Therefore, when the compressor main body operates at high speed, the supply amount of the lubricating oil can be suppressed, and the OCR can be prevented from rising too much.

  In a compressor according to a ninth aspect of the present invention, in the seventh or the eighth aspect, the control unit is configured to, when at least one of the rotation speed and the pressure falls below a predetermined lower limit reference value, The opening degree of the first flow control valve and the second flow control valve is adjusted such that the flow rate of the fluid supplied from one suction pipe is smaller than the flow rate of the fluid supplied from the second suction pipe. You may.

  According to such a configuration, when the compressor body operates at a low speed, the supply amount of the fluid containing almost no lubricating oil decreases, and the supply amount of the fluid containing much lubricating oil increases. Therefore, when the compressor body operates at a low speed, the supply amount of the lubricating oil can be increased, and the OCR can be prevented from being excessively reduced.

  According to the present invention, the lubricating oil supply state can be maintained in an appropriate state.

It is a longitudinal section of a compressor concerning a first embodiment of the present invention. It is a top view of the compressor concerning a first embodiment of the present invention. It is a sectional view of an important section of a compressor concerning a first embodiment of the present invention. It is a longitudinal section of a compressor concerning a second embodiment of the present invention. It is a sectional view of an important section of a compressor concerning a second embodiment of the present invention. It is a longitudinal section of a compressor concerning a third embodiment of the present invention. It is a sectional view of an important section of a modification of the compressor concerning a third embodiment of the present invention.

<< First Embodiment >>
A first embodiment of the present invention will be described with reference to FIGS. The compressor 1 is, for example, a scroll compressor connected to a refrigerant circuit of a refrigeration apparatus and used when compressing a refrigerant gas as a fluid. As shown in FIG. 1, a compressor 1 according to the present embodiment includes a casing 10, a rotating shaft 20, a bearing 30, a refueling pump 40, a driving unit 50, a compressor main body 60, and a bush assembly 70. , A plurality of suction pipes 80, a discharge pipe 90, a first flow control valve 110, a second flow control valve 120, a sensor unit 130, and a control unit 140.

  The casing 10 has a closed-bottomed cylindrical shape. Inside the casing 10, there is formed a space in which various components are arranged. The casing 10 extends in an axial direction Da in which an axis O1 of the rotating shaft 20 described later extends. The casing 10 of the present embodiment is arranged such that the axis direction Da is vertical. The casing 10 houses therein the rotating shaft 20, the bearing 30, the oil supply pump 40, the driving unit 50, the compressor main body 60, the bush assembly 70, and the sensor unit 130. Lubricating oil is stored at the bottom of the casing 10. The interior of the casing 10 is partitioned by the compressor body 60 into a discharge chamber 11 and a suction chamber 12. The discharge chamber 11 is a space in which the compressed cooling gas exists. The discharge chamber 11 is a space in the casing 10 above the compressor main body 60. The suction chamber 12 is a space in which the cooling gas before compression exists. The suction chamber 12 is a space in the casing 10 below the compressor main body 60.

  The rotating shaft 20 has a rotating shaft main body 21 and an eccentric shaft 22. The rotating shaft main body 21 has a cylindrical shape centered on the axis O1. The rotating shaft main body 21 extends in the axial direction Da within the casing 10. The rotating shaft main body 21 is supported by the bearing 30 so as to be rotatable around the axis O1. Inside the rotary shaft main body 21, a rotary shaft main body through hole 211 penetrating the rotary shaft main body 21 in the axial direction Da is formed so as to open at both ends in the axial direction Da.

  The eccentric shaft 22 is integrally provided at one end (upper side in the vertical direction) of the rotary shaft main body 21 in the axial direction Da. The eccentric shaft 22 has an eccentric axis O2 extending in the axial direction Da at a position offset (eccentric) with respect to the axis O1 as a center axis. The eccentric shaft 22 has a column shape smaller than the outer diameter of the rotary shaft main body 21 and having a shorter length in the axial direction Da. Therefore, the eccentric shaft 22 revolves around the axis O1 when the rotation shaft main body 21 rotates around the axis O1. An eccentric shaft through hole 221 is formed inside the eccentric shaft 22 so as to penetrate the eccentric shaft 22 in the axial direction Da. The eccentric shaft through-hole 221 communicates with the rotary shaft main body through-hole 211.

  The bearing part 30 supports the rotating shaft 20 rotatably. The bearing section 30 of the present embodiment has a main bearing 31, a sub bearing 32, and a boss bearing 33.

  The main bearing 31 rotatably supports one end of the rotating shaft main body 21 in the axial direction Da. The main bearing 31 is fixed to an inner wall of the casing 10. The main bearing 31 is connected to the rotary shaft main body through hole 211 via a main oil supply hole 212 formed in the rotary shaft main body 21.

  The sub bearing 32 rotatably supports the other end of the rotating shaft main body 21 in the axial direction Da. The sub-bearing 32 is disposed on the other side (the lower side in the vertical direction) of the main bearing 31 in the axial direction Da. The sub bearing 32 is fixed to the inner wall of the casing 10. The sub bearing 32 is connected to the rotary shaft main body through hole 211 via a sub oil supply hole 213 formed in the rotary shaft main body 21.

  The boss bearing 33 is arranged so as to cover the eccentric shaft 22. Therefore, the boss bearing 33 is arranged on one side in the axial direction Da with respect to the main bearing 31. The boss bearing 33 rotatably supports the eccentric shaft 22 via a bush assembly 70.

  The refueling pump 40 is provided below the sub bearing 32. The oil supply pump 40 pumps up the lubricating oil stored in the casing 10 and supplies the lubricating oil to the main bearing 31, the sub bearing 32, and the boss bearing 33. Specifically, the refueling pump 40 is provided on one side in the axial direction Da of the eccentric shaft 22 from the other end face in the axial direction Da of the rotating shaft main body 21 through the rotating shaft main body through hole 211 and the eccentric shaft through hole 221. Lubricating oil is pumped up to the end face. Lubricating oil flowing through the rotary shaft main body through hole 211 is supplied to the main bearing 31 via the main oil supply hole 212. The lubricating oil flowing through the rotary shaft main body through hole 211 is supplied to the sub bearing 32 via the sub oil supply hole 213. The lubricating oil flowing from the end face of the eccentric shaft 22 is supplied to the boss bearing 33.

  The drive unit 50 is disposed in the casing 10 between the main bearing 31 and the sub-bearing 32 in the axial direction Da. The drive unit 50 is arranged so as to surround the outer peripheral surface at the center of the rotary shaft main body 21. The driving unit 50 drives the rotation shaft main body 21 to rotate. The drive unit 50 is, for example, a motor having a rotor 51 fixed to the outer peripheral surface of the rotating shaft main body 21 and a stator 52 that surrounds the rotor 51 from the outer peripheral side around the axis O1. The rotor 51 has a permanent magnet inside, and its outer shape is substantially cylindrical with the axis O1 as the center. In addition, the drive part 50 should just be able to rotationally drive the rotating shaft 20, and is not limited to a motor.

  The compressor main body 60 is disposed in the casing 10 on one side of the main bearing 31 in the axial direction Da. The compressor body 60 has a fixed scroll 61 and an orbiting scroll 62.

  The fixed scroll 61 is fixed to the inner wall of the casing 10. The fixed scroll 61 has a fixed scroll end plate 611 and a fixed wrap 612.

  The fixed scroll end plate 611 is a disk-shaped plate fixed to the casing 10. The fixed scroll end plate 611 faces the orbiting scroll 62. The fixed scroll end plate 611 has a discharge port 66. The discharge port 66 is a hole formed to pass through the center of the fixed scroll end plate 611. The discharge port 66 discharges the high-pressure refrigerant gas (high-pressure fluid) compressed by the compressor body 60 to the discharge chamber 11.

  The fixed wrap 612 extends from a surface (lower surface) of the fixed scroll end plate 611 facing the other side in the axial direction Da. The fixing wrap 612 is a wall formed in a spiral shape when viewed from the axial direction Da. The fixed wrap 612 is, for example, a plate-shaped member wound around the center of the fixed scroll end plate 611.

  The orbiting scroll 62 is arranged between the fixed scroll 61 and the main bearing 31. The orbiting scroll 62 has an orbiting scroll end plate 621, an orbiting wrap 622, and a boss 623.

  The orbiting scroll end plate 621 is a disk-shaped plate. The orbiting scroll end plate 621 faces the fixed scroll end plate 611 in the axial direction Da.

  The orbiting wrap 622 extends from a surface of the orbiting scroll end plate 621 facing one side in the axial direction Da. The turning wrap 622 is a wall formed in a spiral shape when viewed from the axial direction Da. The orbiting wrap 622 is, for example, a plate-shaped member wound around the center of the orbiting scroll end plate 621.

  The turning wrap 622 is arranged so as to mesh with the fixed wrap 612. Thereby, a compression chamber, which is a space for compressing fluid, is defined between the turning wrap 622 and the fixed wrap 612. As the orbiting wrap 622 orbits with respect to the fixed scroll 61, the volume of the compression chamber changes. Thereby, the fluid (refrigerant gas) in the compression chamber is compressed.

  The boss portion 623 is provided at the center of a surface of the orbiting scroll end plate 621 facing the end surface of the rotary shaft main body 21 facing the other side in the axial direction Da. The boss portion 623 protrudes from the orbiting scroll end plate 621 toward the main bearing 31 so as to form a cylindrical shape. The boss 623 is arranged so as to surround the outer periphery of the eccentric shaft 22. The boss bearing 33 is fixed to the inner peripheral surface of the boss 623.

  The bush assembly 70 connects the orbiting scroll 62 and the rotating shaft 20. The bush assembly 70 is provided between the boss 623 and the eccentric shaft 22. The eccentric shaft 22 is rotatable with respect to the boss 623 by the bush assembly 70 being rotatably supported by the boss bearing 33.

  The casing 10 further includes a storage section 13, a lubricating oil supply path 14, a lubricating oil discharge path 15, and a guide member 16.

  The storage section 13 is a space at the bottom where the lubricating oil in the casing 10 is stored. The storage unit 13 is a part of a region on the other side in the axial direction Da with respect to the driving unit 50 in the casing 10. In the storage unit 13, an oil supply pump 40 is disposed so as to be immersed in the stored lubricating oil.

  The lubricating oil supply path 14 is a passage through which the lubricating oil passes when the lubricating oil is supplied from the storage 13 to the sub bearing 32, the main bearing 31, and the boss bearing 33. The lubricating oil supply path 14 of the present embodiment is the oil supply pump 40, the rotary shaft main body through hole 211, the sub oil supply hole 213, the main oil supply hole 212, and the eccentric shaft through hole 221.

  The lubricating oil discharge path 15 is a passage through which the lubricating oil passes when the lubricating oil used in the sub bearing 32, the main bearing 31, and the boss bearing 33 returns to the storage unit 13. The lubricating oil used in the sub-bearing 32 flows into the space between the sub-bearing 32 and the drive unit 50 in the casing 10 and then flows down into the storage unit 13. Therefore, the lubricating oil discharge path 15 through which the lubricating oil used in the sub-bearing 32 flows is a space on the other side in the axial direction Da with respect to the drive unit 50. Further, the lubricating oil used in the main bearing 31 and the boss bearing 33 flows out into the space between the main bearing 31 and the drive unit 50, and then flows between the drive unit 50 and the inner wall of the casing 10 to be stored therein. It flows down to the part 13. Therefore, the lubricating oil discharge path 15 through which the lubricating oil used in the main bearing 31 and the boss bearing 33 flows is provided between the space between the main bearing 31 and the drive unit 50 and the space between the drive unit 50 and the inner wall of the casing 10. And the space on the other side in the axial direction Da with respect to the driving unit 50.

  The guide member 16 is a member that forms a part of the lubricating oil discharge path 15 and guides the lubricating oil to the storage unit 13. The guide member 16 is provided in a space between the main bearing 31 and the drive unit 50. The guide member 16 is fixed to the casing 10. The guide member 16 of the present embodiment is formed by a plate-shaped member. The guide member 16 guides the lubricating oil that has flowed into the space between the main bearing 31 and the drive unit 50 toward the inner wall of the casing 10 so as not to flow directly onto the drive unit 50. Therefore, the lubricating oil that has flowed into the space between the main bearing 31 and the drive unit 50 flows along the guide member 16 to the space between the drive unit 50 and the inner wall of the casing 10.

  The suction pipe 80 is a pipe for introducing a refrigerant gas before compression into the casing 10 from a supply source (for example, an accumulator, not shown) outside the casing 10. The suction pipe 80 has a first suction pipe 81 and a second suction pipe 82. Only a gas such as a refrigerant gas is introduced from the suction pipe 80, and another pipe (not shown) is used when introducing a liquid such as a liquid-phase refrigerant or lubricating oil into the casing 10.

  The refrigerant gas supplied from the supply source flows into the first suction pipe 81. The first suction pipe 81 is located at a position apart in the axial direction Da with respect to the suction port 65 which is an inlet of the refrigerant gas in the compressor main body 60 and at a position closer to the drive unit 50 than the compressor main body 60. , And the casing 10. Specifically, the first suction pipe 81 is connected to the casing 10 between the drive unit 50 and the main bearing 31 at a position closer to the drive unit 50 than the main bearing 31 in the axial direction Da.

  The refrigerant gas supplied from the supply source flows into the second suction pipe 82 as in the first suction pipe 81. Therefore, the component of the refrigerant gas flowing through the second suction pipe 82 is the same as the component of the refrigerant gas flowing through the first suction pipe 81. The second suction pipe 82 is connected to the casing 10 at a position relatively easily contacted with the lubricating oil with respect to a connection position of the first suction pipe 81 to the casing 10. Specifically, the second suction pipe 82 of the present embodiment is connected to the casing 10 at a position between the main bearing 31 and the drive unit 50 and at a position overlapping the guide member 16 in the axial direction Da. Thereby, the second suction pipe 82 is connected to the casing 10 at a position facing the lubricating oil discharge path 15. The second suction pipe 82 is connected to the casing 10 at a position closer to the main bearing 31 than the drive unit 50 in the axial direction Da. Therefore, the second suction pipe 82 of the present embodiment is connected to the casing 10 at a position closer to the suction port 65 than the first suction pipe 81 is.

  As shown in FIG. 2, the second suction pipe 82 is provided at a different position so that the circumferential position around the axis O <b> 1 does not overlap with the first suction pipe 81 when viewed from the axial direction Da. Have been. As shown in FIG. 3, the diameter of the second suction pipe 82 is smaller than the diameter of the first suction pipe 81. The diameter of the second suction pipe 82 is preferably less than half the diameter of the first suction pipe 81. Specifically, when the diameter of the first suction pipe 81 is about φ20, the diameter of the second suction pipe 82 is less than φ10.

  The discharge pipe 90 is provided at the top, which is one end of the casing 10 in the axial direction Da. The discharge pipe 90 communicates with the discharge chamber 11. From the discharge pipe 90, the high-pressure refrigerant gas compressed by the compressor body 60 and discharged from the discharge port 66 to the discharge chamber 11 is discharged. The discharge pipe 90 is connected to a use destination (for example, an indoor unit, not shown) of the compressed refrigerant gas.

  The first flow control valve 110 is capable of adjusting the flow rate of the fluid flowing through the first suction pipe 81. The first flow control valve 110 allows the refrigerant gas to flow into the casing 10 from the first suction pipe 81 when opened. The first flow control valve 110 stops the flow of the refrigerant gas from the first suction pipe 81 into the casing 10 by being closed.

  The second flow control valve 120 is capable of adjusting the flow rate of the fluid flowing through the second suction pipe 82. The second flow control valve 120 allows the refrigerant gas to flow into the casing 10 from the second suction pipe 82 by being opened. The second flow control valve 120 stops the flow of the refrigerant gas from the second suction pipe 82 into the casing 10 by being closed.

  The sensor unit 130 is a measuring device that can measure at least one of the rotation speed of the rotating shaft 20 and the pressure of the compressor main body 60. The sensor unit 130 of the present embodiment is, for example, a device that measures the number of rotations of the rotating shaft main body 21. The sensor unit 130 is disposed in the casing 10. The sensor unit 130 outputs data of the measurement result to the control unit 140.

  The control unit 140 adjusts the opening of the first flow control valve 110 and the second flow control valve 120 according to the measurement result of the sensor unit 130. The control unit 140 opens or closes the first flow control valve 110 and the second flow control valve 120 when the input measurement result satisfies a predetermined condition. Specifically, the control unit 140 sends an instruction to open the first flow control valve 110 when the number of revolutions input as a measurement result exceeds a predetermined upper limit reference value. At this time, the controller 140 sends an instruction to the second flow control valve 120 to close the second flow control valve 120. Thereby, when the rotation speed exceeds the upper limit reference value, the refrigerant gas does not flow into the casing 10 from the second suction pipe 82, but flows only from the first suction pipe 81. That is, when the rotation speed exceeds the upper limit reference value, the flow rate of the refrigerant gas supplied from the first suction pipe 81 becomes larger than the flow rate of the refrigerant gas supplied from the second suction pipe 82.

  In addition, the control unit 140 sends an instruction to open the second flow control valve 120 when the number of revolutions input as a measurement result falls below a predetermined lower limit reference value. At this time, the control unit 140 sends an instruction to close the first flow control valve 110. Thereby, when the rotation speed falls below the lower limit reference value, the refrigerant gas does not flow into the casing from the first suction pipe 81, but flows only from the second suction pipe 82. That is, when the rotation speed falls below the lower limit reference value, the flow rate of the refrigerant gas supplied from the second suction pipe 82 becomes larger than the flow rate of the refrigerant gas supplied from the first suction pipe 81.

  In addition, when the rotation speed input as the measurement result is equal to or less than the upper reference value and equal to or greater than the lower reference value, the control unit 140 opens both the first flow control valve 110 and the second flow control valve 120. Send instructions to release them. Thereby, when the rotation speed is between the upper reference value and the lower reference value, the refrigerant gas flows into the casing 10 from both the first suction pipe 81 and the second suction pipe 82. Even in this state, since the pipe diameter of the first suction pipe 81 is larger than that of the second suction pipe 82, the flow rate of the refrigerant gas supplied from the first suction pipe 81 is smaller than that of the refrigerant supplied from the second suction pipe 82. More than the gas flow.

  Here, the upper limit reference value is the number of rotations of the rotary shaft 20 that can be regarded as the high speed operation of the compressor main body 60. Conversely, the lower limit reference value is the number of rotations of the rotating shaft 20 that can be regarded as the low speed operation of the compressor main body 60.

  According to the compressor 1 as described above, the first suction pipe 81 and the second suction pipe 82 are provided as the suction pipe 80. By providing a plurality of suction pipes 80, the influence of the refrigerant gas flowing from each suction pipe 80 can be suppressed as compared with the case where only one suction pipe 80 is provided. As a result, fluctuations in OCR due to the refrigerant gas supplied from each suction pipe 80 can be suppressed.

  Further, the second suction pipe 82 is connected to the casing 10 at a position where the second suction pipe 82 relatively easily comes into contact with the lubricating oil with respect to the first suction pipe 81. Therefore, the refrigerant gas flowing from the second suction pipe 82 is more lubricating oil before reaching the suction port 65 of the compressor body 60 than the refrigerant gas flowing from the first suction pipe 81. In other words, the refrigerant gas supplied from the first suction pipe 81 and the refrigerant gas supplied from the second suction pipe 82 are sent to the suction port 65 of the compressor main body 60 with the lubricating oil amounts being different from each other. The ability to supply refrigerant gas containing different amounts of lubricating oil facilitates increasing and decreasing the OCR. As a result, the OCR in the casing 10 can be easily managed. Accordingly, the lubricating oil supply state can be maintained in an appropriate state regardless of the operation state of the compressor main body 60.

  The diameter of the second suction pipe 82 is smaller than that of the first suction pipe 81. Therefore, more refrigerant gas flows into the casing 10 from the first suction pipe 81 than from the second suction pipe 82. Therefore, the supply amount of the refrigerant gas containing less lubricating oil is larger than the supply amount of the refrigerant gas containing more lubricating oil. During high-speed operation of the compressor body 60, the OCR value is likely to increase, so that it is preferable to supply a refrigerant gas containing little lubricating oil. Furthermore, at the time of high-speed operation, it is preferable that a large amount of refrigerant gas be supplied in order to use the compressor body 60 as efficiently as possible. Therefore, since the first suction pipe 81 supplies a large amount of refrigerant gas containing little lubricating oil, the operation performance of the compressor body 60 during high-speed operation can be stabilized.

  The first suction pipe 81 is connected to the casing 10 at a position closer to the drive unit 50 than the compressor main body 60 so as to be largely separated from the suction port 65 of the compressor main body 60 in the axial direction Da. Further, the first suction pipe 81 is connected to the casing 10 at a position deviated from the lubricating oil supply path 14 which is a lubricating oil distribution path between the storage section 13 and the bearing section 30. Therefore, even if the lubricating oil is contained in the refrigerant gas supplied from the first suction pipe 81 into the casing 10, the lubricating oil is separated from the refrigerant gas before reaching the suction port 65. As a result, the refrigerant gas containing less lubricating oil can be supplied to the suction port 65.

  The connection position of the second suction pipe 82 with the casing 10 is arranged so as to face the lubricating oil discharge path 15. Therefore, the refrigerant gas supplied from the second suction pipe 82 into the casing 10 reaches the suction port 65 after passing through the lubricating oil flowing through the lubricating oil discharge path 15. As a result, the amount of lubricating oil contained in the refrigerant gas flowing into the casing 10 from the second suction pipe 82 increases. Therefore, the refrigerant gas containing a large amount of lubricating oil can be supplied to the suction port 65.

  Further, instead of the lubricating oil immediately before being supplied to the bearing unit 30 as in the lubricating oil supply path 14, the refrigerant gas is passed through the lubricating oil discharge path 15 through which the lubricating oil used in the bearing unit 30 flows. . As a result, it is possible to suppress the occurrence of a problem such as a decrease in the amount of lubricating oil supplied to the bearing unit 30 that impairs the reliability of the bearing unit 30. Therefore, the reliability of the bearing 30 can be maintained.

  Further, the second suction pipe 82 is connected to the casing 10 at a position overlapping the guide member 16 in the axial direction Da among the positions facing the lubricating oil discharge path 15. Therefore, the refrigerant gas flowing into the casing 10 from the second suction pipe 82 passes through the lubricating oil flowing between the guide member 16 and the inner wall of the casing 10. Therefore, the refrigerant gas more easily comes into contact with the lubricating oil. Thereby, the refrigerant gas containing more lubricating oil can be supplied to the suction port 65.

  Further, the flow rate of the refrigerant gas flowing through the first suction pipe 81 can be adjusted by the first flow rate adjustment valve 110. Further, the flow rate of the refrigerant gas flowing through the second suction pipe 82 can be adjusted by the second flow rate adjustment valve 120. The opening and closing of the first flow control valve 110 and the second flow control valve 120 is controlled by the control unit 140 according to the rotation speed of the rotating shaft main body 21. The opening and closing of the first flow control valve 110 and the second flow control valve 120 are controlled in accordance with the rotation speed of the rotary shaft main body 21, so that the first suction pipe 81 and the second Which of the two suction pipes 82 is supplied with the refrigerant gas can be adjusted. Therefore, the supply amount of the refrigerant gas supplied from the first suction pipe 81 and the supply amount of the refrigerant gas supplied from the second suction pipe 82 can be adjusted according to the operation state of the compressor main body 60.

  In particular, in this embodiment, when the rotation speed exceeds the upper limit reference value, the first flow control valve 110 is opened and the second flow control valve 120 is closed. Therefore, when the compressor body 60 operates at high speed, the refrigerant gas containing a large amount of lubricating oil is not supplied, and only the refrigerant gas containing little lubricating oil is supplied to the suction port 65. Therefore, when the compressor main body 60 operates at a high speed, the supply amount of the lubricating oil can be suppressed, and the OCR can be prevented from rising excessively.

  Further, when the rotation speed falls below the lower limit reference value, the second flow control valve 120 is opened and the first flow control valve 110 is closed. Therefore, when the compressor body 60 operates at a low speed, the refrigerant gas containing almost no lubricating oil is not supplied, and only the refrigerant gas containing much lubricating oil is supplied to the suction port 65. Therefore, when the compressor main body 60 operates at a low speed, the supply amount of the lubricating oil can be increased, and the OCR can be prevented from falling too much.

<< Second embodiment >>
Next, a compressor according to a second embodiment of the present invention will be described with reference to FIGS. In the compressor shown in the second embodiment, the connection position of the second suction pipe to the casing is different from that of the first embodiment. Therefore, in the description of the second embodiment, the same portions as those of the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  As shown in FIGS. 4 and 5, in the compressor 1A of the second embodiment, the suction pipe 80A has a first suction pipe 81 and a second suction pipe 82A. The second suction pipe 82 </ b> A is connected to the casing 10 at a position facing the storage unit 13. Therefore, the connection position of the second suction pipe 82 </ b> A with the casing 10 is located on the other side in the axial direction Da (downward in the vertical direction) from the level of the lubricating oil stored in the storage section 13. That is, the second suction pipe 82 </ b> A of the second embodiment is connected to the casing 10 at a position farther than the first suction pipe 81 with respect to the suction port 65. The refrigerant gas supplied from the second suction pipe 82A into the casing 10 is sent into the stored lubricating oil.

  According to the compressor 1A of the second embodiment, the refrigerant gas supplied into the casing 10 from the second suction pipe 82A reaches the suction port 65 after passing through the lubricating oil stored in the storage unit 13. I do. As a result, the amount of lubricating oil contained in the refrigerant gas flowing into the casing 10 from the second suction pipe 82A greatly increases. Therefore, the refrigerant gas containing a large amount of lubricating oil can be supplied to the suction port 65.

  Further, instead of the lubricating oil immediately before being supplied to the bearing unit 30 as in the storage unit 13, the refrigerant gas is passed through the lubricating oil stored after use in the bearing unit 30. As a result, it is possible to suppress the occurrence of a problem such as a decrease in the amount of lubricating oil supplied to the bearing unit 30 that impairs the reliability of the bearing unit 30. Therefore, the reliability of the bearing 30 can be maintained.

<< Third embodiment >>
Next, a compressor according to a third embodiment of the present invention will be described with reference to FIG. In the compressor shown in the third embodiment, the connection position of the first suction pipe to the casing and the number of the first suction pipes are different from those of the first embodiment. Therefore, in the description of the third embodiment, the same portions as those of the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  As shown in FIG. 6, in the compressor 1B of the third embodiment, the suction pipe 80B has a plurality of (two) first suction pipes 81B and a second suction pipe 82. The first suction pipe 81 </ b> B is connected to the casing 10 at a radially outer side centering on the rotation shaft 20 with respect to the suction port 65. The first suction pipe 81B is connected to the casing 10 on one side of the main bearing 31 in the axial direction Da in the axial direction Da. Therefore, the first suction pipe 81B of the third embodiment is connected to the casing 10 at a position closer to the suction port 65 than the second suction pipe 82. The two first suction pipes 81B are arranged so that the positions in the circumferential direction are different from each other by 180 °.

  According to the compressor 1B of the third embodiment, the refrigerant gas supplied into the casing 10 from the first suction pipe 81B does not pass through the space in the casing 10 through which the lubricating oil flows, but at the shortest distance from the suction port. 65. Therefore, it is possible to suppress the lubricating oil flowing through the casing 10 from being caught in the refrigerant gas flowing into the casing 10 from the first suction pipe 81B. As a result, the refrigerant gas containing less lubricating oil can be supplied to the suction port 65.

  Further, since the number of the first suction pipes 81B is larger than the number of the second suction pipes 82, the supply amount of the refrigerant gas containing no lubricating oil is larger than the supply amount of the refrigerant gas containing more lubricating oil. . Therefore, for example, even if the compressor main body 60 is a large-capacity scroll compressor that requires a large amount of refrigerant gas during high-speed operation, the supply state of the lubricating oil can be maintained in an appropriate state.

(Other Modifications of Embodiment)
As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, each configuration and a combination thereof in each embodiment is an example, and addition or omission of a configuration may be performed without departing from the gist of the present invention. , Substitutions, and other changes are possible. The present invention is not limited by the embodiments, but is limited only by the claims.

  That is, the compressors 1, 1A, and 1B of the present invention may have a configuration in which any of the above-described embodiments is combined. For example, in a compressor 1C of a modified example of the third embodiment, as shown in FIG. 7, the suction pipe 80C may have one first suction pipe 81B and one second suction pipe 82. Therefore, in the compressor 1C of the modified example, only the first suction pipe 81B connected to the casing 10 right beside the suction port 65 is provided so as to directly communicate with the suction port 65. In this modification, the refrigerant gas flowing from the first suction pipe 81B flows almost directly into the suction port 65 without flowing through the casing 10. As described above, the first suction pipes 81 and 81B and the second suction pipes 82 and 82A may be provided only one each, or may be provided plurally, and only one of them is provided as in the third embodiment. May be provided in plurality.

  Further, the compressor main body 60 is not limited to a scroll compressor as in the present embodiment. The compressor main body 60 may be, for example, a rotary compressor.

  Further, the guide member 16 is not limited to the shape as in the present embodiment. The guide member 16 only needs to be able to guide the lubricating oil to the storage unit 13 so that the lubricating oil does not flow directly onto the driving unit 50. Therefore, the guide member 16 may be, for example, a tubular pipe. At this time, the second suction pipe 82 is connected to the casing 10, for example, near the outlet of the cylindrical pipe.

  In addition, the first flow rate control valve 110 and the second flow rate control valve 120 are not limited to the degree of opening being adjusted to be completely opened or completely closed. The opening degree of the first flow control valve 110 and the second flow control valve 120 may be adjusted so as to reduce or open the flow so that a certain amount of refrigerant gas flows.

  Further, the sensor unit 130 is not limited to a device that measures the number of rotations. The sensor unit 130 may be any device that can detect the operating state of the compressor main body 60. Therefore, the sensor unit 130 may be, for example, a device that measures the pressure of the compressed refrigerant gas discharged from the discharge port 66 of the compressor main body 60 and the pressure in the casing 10.

1, 1A, 1B, 1C Compressor 10 Casing 11 Discharge chamber 12 Suction chamber 13 Reservoir 14 Lubricating oil supply path 15 Lubricating oil discharge path 16 Guide member 20 Rotary shaft 21 Rotary shaft main body 211 Rotary shaft main body through hole 212 Main oil supply hole 213 Sub oil supply hole 22 Eccentric shaft 221 Eccentric shaft through hole O1 Axis O2 Eccentric axis Da Axial direction 30 Bearing unit 31 Main bearing 32 Sub bearing 33 Boss bearing 40 Oil pump 50 Drive unit 51 Rotor 52 Stator 60 Compressor body 61 Fixed scroll 611 Fixed scroll end plate 612 Fixed wrap 62 Revolving scroll 621 Revolving scroll end plate 622 Revolving wrap 623 Boss portion 65 Suction port 70 Discharge port 70 Bush assembly 80, 80A, 80B, 80C Suction pipe 81, 81B First suction pipe 82, 82A Two suction pipes 90 Discharge pipes 110 First flow Adjusting valve 120 a second flow rate adjusting valve 130 sensor unit 140 control unit

Claims (9)

An axis of rotation extending along the axis;
A bearing portion rotatably supporting the rotating shaft,
A drive unit that drives the rotation shaft to rotate,
A compressor body that compresses a fluid by being rotated by the rotating shaft,
A casing in which the rotating shaft, the drive unit and the compressor body are housed, and lubricating oil for lubricating the bearing unit is stored therein;
A plurality of suction pipes for supplying a fluid before compression into the casing,
The plurality of suction pipes,
A first suction pipe connected to the casing,
A compressor having a second suction pipe connected to the casing at a position where the first suction pipe is relatively easily contacted with the lubricating oil with respect to a connection position with respect to the casing in the first suction pipe.   The compressor according to claim 1, wherein a pipe diameter of the second suction pipe is smaller than a pipe diameter of the first suction pipe.   The first suction pipe is connected to the casing at a position apart from the suction port of the compressor main body in an axial direction in which the rotation shaft extends and closer to the drive unit than the compressor main body. The compressor according to claim 1 or 2, wherein   The first suction pipe according to any one of claims 1 to 3, wherein the first suction pipe is connected to the casing at a radially outer side about the rotation axis with respect to a suction port of the compressor body. The compressor as described. The casing is
A storage unit in which the lubricating oil is stored,
A lubricating oil supply path through which the lubricating oil is supplied from the storage section to the bearing section,
A lubricating oil discharge path for sending the lubricating oil used in the bearing unit from the bearing unit to the storage unit,
The compressor according to any one of claims 1 to 4, wherein the second suction pipe is connected to the casing at a position facing at least one of the lubricating oil discharge path and the storage section. The casing has a guide member that forms a part of the lubricating oil discharge path and guides the lubricating oil to the reservoir.
The compressor according to claim 5, wherein the second suction pipe is connected to the casing at a position overlapping the guide member in an axial direction in which the rotation shaft extends. A first flow control valve capable of adjusting the flow rate of the fluid flowing through the first suction pipe,
A second flow rate adjustment valve capable of adjusting the flow rate of the fluid flowing through the second suction pipe,
7. The controller according to claim 1, further comprising a controller configured to adjust an opening of the first flow control valve and the second flow control valve in accordance with at least one of a rotation speed of the rotation shaft and a pressure of the compressor body. 8. A compressor according to any one of the preceding claims.   The control unit, when at least one of the rotation speed and the pressure exceeds a predetermined upper limit reference value, the flow rate of the fluid supplied from the first suction pipe is supplied from the second suction pipe The compressor according to claim 7, wherein an opening of each of the first flow control valve and the second flow control valve is adjusted to be larger than a flow rate of the fluid.   The control unit, when at least one of the rotation speed and the pressure is lower than a predetermined lower limit reference value, the flow rate of the fluid supplied from the first suction pipe is supplied from the second suction pipe 9. The compressor according to claim 7, wherein the openings of the first flow control valve and the second flow control valve are adjusted so as to be smaller than the flow rate of the fluid. 10.

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