JP2005337210A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary compressor which is small but can materialize large displacement. <P>SOLUTION: A compression mechanism part compressing gas in the rotary compressor is constructed to arrange a plurality of cylinders including a cylindrical inner surface and having a rotor 14 provided therein adjacently in an axial direction under a condition where a separator 13 is put therebetween. A crankshaft is inserted in the cylinders, the separator 13 and the rotor 14. The crankshaft 16 has a structure connecting a first unit 16a and a second unit 16b provided on an eccentric shaft part 17 engaging with the rotor 14. An opening part 13a having a smaller diameter than the eccentric shaft part 17 is provided on the separator 13. A connection part 41 of a smaller diameter than the eccentric shaft part 17 is provided on the first unit 16a and the second unit 16b. The separator is connected by the connection part 41 under a condition where the connection part 41 is inserted in the opening part 13a of the separator. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotary compressor.

The rotary compressor is used for compressing a gaseous refrigerant in a refrigerant circuit in an air conditioner such as a room air conditioner or a packaged air conditioner.
As such a rotary compressor, for example, a rotary compressor described in Patent Document 1 described below is known.

This rotary compressor has a sealed case, and a compression mechanism portion composed of a first cylinder and a second cylinder provided in the sealed case.
The first cylinder and the second cylinder are partitioned by a partition plate and are independent of each other. The partition plate is provided with an opening hole, and a shaft is inserted through the opening hole.
The shaft is provided with an eccentric shaft portion in a region accommodated in each cylinder, and a roller is provided on the outer periphery of each eccentric shaft portion.
Each cylinder is provided with a blade that is urged by the urging means and always brought into contact with the outer peripheral surface of the roller, and a space in the cylinder is partitioned by the blade and the roller.

  The rotary compressor rotates the shaft to rotate the roller engaged with the eccentric shaft portion eccentrically in each cylinder, thereby changing the volume of the space partitioned by the blade and the roller in each cylinder. Intake into the cylinder, compression of the atmosphere in each cylinder, and discharge operation of the compressed cylinder atmosphere are repeated continuously.

JP-A-8-144976 (paragraph [0016] and FIGS. 1 and 2)

The rotary compressor is required to have a small size and a large capacity.
As a method of increasing the capacity of the rotary compressor without increasing the outer dimensions, the effective amount in the cylinder is increased by increasing the eccentric amount of the roller engaged with the eccentric shaft portion (that is, the eccentric amount of the eccentric shaft portion). There are ways to increase it.

However, the rotary compressor described in Patent Document 1 is configured on the assumption that the shaft is inserted into the opening of the partition plate by passing the opening of the partition plate through one of the eccentric shaft portions of the shaft. Therefore, the diameter of the opening hole of the partition plate is larger than the diameter of the eccentric shaft portion.
For this reason, in this rotary compressor, on the side opposite to the eccentric direction of the eccentric shaft portion, a gap having a size proportional to the eccentric amount of the eccentric shaft portion is formed between the eccentric shaft portion and the partition plate.

In this rotary compressor, the thickness (diameter thickness) of the roller is set so that the gap is always located within the outer peripheral edge of the roller, and thereby, the space located outside the roller in the radial direction within the cylinder. (Space used for gas compression) and this gap are separated by a roller to prevent the gas compressed in the cylinder from leaking out of the cylinder.
However, when the eccentric amount of the eccentric shaft portion increases, it is necessary to increase the thickness of the roller accordingly. If the thickness of the roller is increased in this way, the effective capacity in the cylinder is reduced accordingly.
As described above, since the conventional rotary compressor cannot increase the eccentric amount of the eccentric shaft portion so much, it is difficult to increase the capacity without increasing the outer dimensions.

  This invention is made | formed in view of such a situation, Comprising: It aims at providing the rotary compressor which can implement | achieve large capacity | capacitance, although it is small.

In order to solve the above problems, the rotary compressor of the present invention employs the following means.
That is, the rotary compressor according to the present invention has a compression mechanism portion that compresses gas and a drive portion that drives the compression mechanism portion, and the compression mechanism portion has a cylindrical inner surface and the rotor is accommodated therein. A plurality of cylinders are arranged adjacent to each other in the axial direction with a separator interposed therebetween, and each cylinder is urged in a direction protruding from the cylindrical inner surface, and the space in the cylinder together with the rotor And a crankshaft that engages with each of the rotors is inserted into each of the cylinders and the separator, and the crankshaft is rotationally driven by the drive unit. Thus, each of the rotors is eccentrically rotated in each of the cylinders to compress the atmosphere in each of the cylinders. The oscillator is provided with an opening through which the crankshaft is inserted, and the crankshaft is configured by connecting a plurality of units each provided with one eccentric shaft portion that engages with the rotor, At least one of the units to be connected is provided with a connecting portion having a smaller diameter than the eccentric shaft portion, and the units to be connected are inserted through the opening of the separator. It is connected by this connection part in the state, It is characterized by the above-mentioned.

  In the rotary compressor configured as described above, each eccentric shaft portion of the crankshaft constituting the compression mechanism portion is provided in a separate unit. And, by placing a separator between these units, and connecting these units with each other in a state where a smaller diameter connecting portion than the eccentric shaft portion is inserted into the opening of the separator, each eccentric shaft portion A crankshaft having a separator disposed therebetween is formed.

That is, in the rotary compressor according to the present invention, it is not necessary to pass the eccentric shaft portion through the opening portion of the separator during assembly, so that the size of the opening portion can be significantly reduced.
Thereby, the eccentric amount of the eccentric shaft portion can be made larger than before, and the capacity of the rotary compressor can be increased without increasing the outer shape.

Further, in the rotary compressor configured as described above, the crankshaft is composed of a plurality of units, and each unit can be processed. Therefore, compared to the case where the crankshaft is composed of a single member. Therefore, the degree of freedom in processing the crankshaft is high.
For this reason, in the rotary compressor according to the present invention, it is possible to improve the productivity of the crankshaft as compared with the conventional one, or to easily realize a configuration that is impossible or difficult to realize with the conventional one-piece crankshaft. Can do. For example, in the rotary compressor according to the present invention, by providing an oil supply path in different units, an independent oil supply path can be easily provided for each region located in each cylinder in the crankshaft.

  In this rotary compressor, a bearing that supports the connecting portion may be provided in the opening of the separator.

  In the rotary compressor configured as described above, since the crankshaft is supported by the bearing even in the region between the eccentric shaft portions, the crankshaft is not easily bent during the operation of the rotary compressor, and the reliability is high.

  Here, in the conventional rotary compressor, the crankshaft having the eccentric shaft portion is constituted by a single member, and the bearing cannot be passed through the eccentric shaft portion, so the region between the eccentric shaft portions of the crankshaft The bearing cannot be mounted on. For this reason, in the conventional rotary compressor, only the end portion of the crankshaft is supported by the bearing.

On the other hand, the rotary compressor according to the present invention has a structure in which the crankshaft is connected to a plurality of units each having an eccentric shaft portion as described above, and each unit has a smaller diameter than the eccentric shaft portion. The parts are connected by this connecting part in a state of being inserted through the opening of the separator.
For this reason, a connecting portion is inserted into a bearing provided in the opening of the separator, and each unit is connected in this state, thereby forming a crankshaft in which the connecting portion is supported by the separator via the bearing. That is, the configuration of the present invention is a novel configuration that can be realized only by adopting the configuration of the first aspect.

  In the rotary compressor, the crankshaft may be provided with a lubricating oil supply path for supplying lubricating oil to a sliding surface with the bearing.

  Here, generally, a rotary compressor is provided with a lubricating oil supply mechanism that supplies lubricating oil into each cylinder, and in each cylinder, the lubricating oil supplied by this lubricating oil supply mechanism is provided. Thus, lubrication and sealing between the cylinder inner surface and the rotor are performed. This lubricating oil supply mechanism is generally configured to supply lubricating oil into each cylinder using an oil hole provided in the crankshaft.

In the rotary compressor according to the present invention, the crankshaft is provided with a lubricating oil supply path. For this reason, the lubricating oil can be supplied to the bearing using a conventional lubricating oil supply mechanism, and the lubricating oil can be supplied to the bearing with a simple structure.
Here, when the rotary compressor is a rotary compressor (vertical rotary compressor) in which the cylinders are arranged in the vertical direction, the lubricating oil supply path is at the upper end of the sliding surface with the bearing. It is preferable to open to the side. As a result, the lubricating oil supplied to the sliding surface from the lubricating oil supply path moves downward due to gravity and is also supplied to the lower end side of the sliding surface, so the lubricating oil is reliably supplied to the entire sliding surface. can do.

  In the rotary compressor, the cylinders are arranged in a vertical direction, and the compressed gas discharged from the cylinder located below is supplied to the separator in the rotary gas flow path. A discharge path that leads to the downstream side of the cylinder, and an oil separator that separates the lubricating oil from the compressed gas fed into the discharge path from the lower cylinder and returns it to the lower cylinder. .

Here, as described above, since the lubricating oil is supplied into each cylinder of the rotary compressor, a part of the lubricating oil is discharged together with the compressed gas from each cylinder.
In a conventional vertical rotary compressor, the lower end of the compression mechanism is covered with a lower muffler, and the lower cylinder of the compression mechanism is temporarily discharged into a space in the lower muffler to generate compressed gas and lubricating oil. After separating and recovering the lubricating oil, the compressed gas from which the lubricating oil was removed was sent to the subsequent stage of the rotary compressor.
For this reason, the conventional vertical rotary compressor requires a space for providing the lower muffler below the compression mechanism.

On the other hand, in the rotary compressor (vertical rotary compressor) according to the present invention, the separator is supplied with the compressed gas discharged from the cylinder located below the downstream of the compressed gas flow path in the rotary compressor. A discharge path leading to the side is provided. The discharge path is provided with an oil separator that separates the lubricating oil from the compressed gas fed into the discharge path and returns it to the lower cylinder.
For this reason, in this rotary compressor, since the lower muffler can be omitted and the dimension of the compression mechanism portion in the height direction can be reduced, further miniaturization is possible.

  Further, in this rotary compressor, the crankshaft is held at one end side by the drive unit, and the driving force of the drive unit is input from the one end side, and the crankshaft among the units constituting the crankshaft The unit constituting the other end side of the crankshaft may be made of a lighter material than the unit constituting the one end side.

In the rotary compressor configured as described above, the other end side of the crankshaft, which has a smaller load than the one end side to which the driving force from the driving unit is input, is configured by a unit made of a lighter material. .
For this reason, in the unit constituting the other end side, the moment of inertia can be kept at the same level as the unit constituting the one end side while increasing the amount of eccentricity of the eccentric shaft portion as compared with the unit constituting the one end side.

  That is, in this rotary compressor, one end of the crankshaft to which the driving force from the drive unit is input is constituted by a unit made of a high-strength material, and the crankshaft is secured while ensuring sufficient durability and reliability. The capacity of the cylinder on the other end side can be further increased from the capacity of the cylinder on the one end side while maintaining a good balance of the moment of inertia when rotating.

  In this rotary compressor, at least some of the cylinders may be connected in series on the gas flow path of the compression mechanism section.

In the rotary compressor configured as described above, in the cylinders connected in series, the compressed gas compressed in the cylinder on the upstream side of the flow path is further compressed in the cylinder on the downstream side. That is, multistage compression is performed by the cylinders connected in series, and the pressure of the compressed gas is increased to the final discharge pressure of the compression mechanism unit (target discharge pressure of the rotary compressor).
In this configuration, the compression ratio of the gas in each of the cylinders connected in series is smaller than that of a rotary compressor configured to obtain a compressed gas having a final discharge pressure by one-stage compression. The pressure difference between the low pressure space (intake side space) and the high pressure side space (discharge side space) in the space partitioned by the rotor and blades in each cylinder is smaller than that of the machine.

For this reason, in this rotary compressor, the leakage of compressed gas from the high-pressure side space to the low-pressure side space in the cylinder is reduced, and the operation efficiency is high. This configuration is particularly effective when used for compression of a refrigerant that requires high compression (for example, a natural refrigerant such as a carbon dioxide refrigerant or an ammonia refrigerant).
Further, when this configuration is applied to the rotary compressor according to claim 5 and the cylinder provided with the unit on one end and the cylinder provided with the unit on the other end are connected in series, the compression of the preceding stage Since the compression ratio can be changed between the cylinder used for the cylinder and the cylinder used for the subsequent compression, more detailed compression conditions can be set according to the nature of the gas to be compressed.

  Moreover, in this rotary compressor, among the cylinders connected in series, the cylinder on the upstream side of the flow path may be disposed on one end side of the crankshaft with respect to the cylinder on the downstream side.

Here, since the compression of the gas in the cylinder is almost adiabatic compression, the temperature of the compressed gas rises. For this reason, in a rotary compressor that performs multi-stage compression, the temperature of the cylinder used for the subsequent stage of compression increases.
On the other hand, a drive motor is generally used as the drive unit of the rotary compressor. However, the coil of the drive motor is vulnerable to heat, causing a dielectric breakdown in a high-temperature environment or unwinding the coil. Inconvenience arises.
In the rotary compressor according to the present invention, since the latter stage cylinder that is at a higher temperature is kept away from the drive unit, damage to the drive unit due to heat can be prevented, and the reliability is high and the life is long.

  Further, in this rotary compressor, the compression mechanism portion has a cylindrical shape with both ends closed, and is installed in a housing in which compressed gas discharged from at least one of the cylinders is temporarily stored, The blade is urged by the internal pressure of the housing in at least the most downstream cylinder of the flow path, and the most downstream cylinder is disposed at an end portion in the axial direction of the housing. The housing is provided with a cylinder partition that partitions a high-pressure area in which the most downstream cylinder is accommodated and an area in which the other cylinder is accommodated. The compressed gas discharged from the cylinder used in the above may be supplied.

Here, in the conventional rotary compressor, the housing in which the compression mechanism unit is accommodated is formed as one continuous space, and in this space, the compression compressed to the final discharge pressure of the compression mechanism unit is performed. Gas is temporarily stored.
However, in this configuration, since the final discharge pressure is applied to the entire housing, the entire housing needs to be strong enough to withstand this high pressure, and the manufacturing cost is high.
On the other hand, in the rotary compressor according to the present invention, since the high pressure side region where the internal pressure is highest is provided at the end of the housing, the housing is provided only at the end portion and the cylinder partition that constitute the high pressure side region. Since it is sufficient to have a strength sufficient to withstand the final discharge pressure, the manufacturing cost can be reduced.

  Further, in this rotary compressor, the compression mechanism section and the drive section are installed in the same housing, and a first area in which the compression mechanism section is disposed in the housing. And a second partition in which the drive unit is provided, and the first region is a space for temporarily storing compressed gas discharged from at least one of the cylinders of the compression mechanism unit. The second region may be a passage through which the gas to be compressed supplied to the rotary compressor passes before being sent into the compression mechanism.

In the rotary compressor configured as described above, the second region in which the drive unit is installed in the housing and the first region in which the compression mechanism unit is provided are partitioned by a main partition wall. The gas to be compressed before being compressed by the compression mechanism, that is, the coldest gas in the rotary compressor is taken in.
That is, in this rotary compressor, the drive unit is isolated from the high-temperature compressed gas pressurized by the compression mechanism unit, and the drive unit is cooled by the coldest gas, so that the drive unit is damaged by heat. Is less likely to occur and is reliable and has a long service life.
Moreover, in this rotary compressor, since the 1st area | region acts as an oil separator, lubricating oil can be collect | recovered from the compressed gas to discharge.

  According to the rotary compressor according to the present invention, a large capacity can be realized while being small.

Embodiments according to the present invention will be described below with reference to the drawings.
[First embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3.
The rotary compressor 1 according to the present embodiment is provided on a refrigerant circuit of an air conditioner such as a room air conditioner or a packaged air conditioner, and is used for compression of a gaseous refrigerant flowing through the refrigerant circuit.
As shown in FIG. 1, the rotary compressor 1 has a housing 2 that is a sealed container, and in the housing 2, a compression mechanism unit 3 that compresses a gaseous refrigerant supplied from a refrigerant circuit, and this The drive part 4 which drives the compression mechanism part 3 is accommodated.

In this embodiment, the housing 2 is a substantially cylindrical sealed container with both ends closed, and is installed with the axis line being substantially vertical. The compression mechanism unit 3 is disposed below the housing 2, and the drive unit 4 is disposed above the compression mechanism unit 3.
In addition, refrigerant pipes P1 and P2 of the refrigerant circuit are inserted from the outside into the lower side surface of the housing 2, and gaseous refrigerant of the refrigerant circuit is supplied to the compression mechanism unit 3 through the refrigerant pipes P1 and P2. ing.
Here, although not shown, the bottom part of the housing 2 stores lubricating oil used for lubricating the compression mechanism unit 3 and the like.

The compression mechanism unit 3 compresses the gaseous refrigerant supplied from the refrigerant pipes P1 and P2 into a high-pressure compressed gas and then sends the compressed gas into the housing 2.
Here, a refrigerant pipe P3 is inserted from the outside into the ceiling portion of the housing 2, and the compressed gas temporarily stored in the housing 2 is sent to the downstream side of the refrigerant circuit through the refrigerant pipe P3. It has become.

The compression mechanism unit 3 includes a plurality of cylinders 11 having a cylindrical inner surface 12, and the cylinders 11 are arranged so that the cylindrical inner surfaces 12 are substantially coaxial with each other and the separator 13 is interposed between the cylinders 11. Adjacently arranged in the axial direction in a sandwiched state.
Inside each cylinder 11, a cylindrical rotor 14 having a diameter smaller than that of the cylindrical inner surface 12 is provided so that its axis is substantially parallel to the axis of the cylindrical inner surface 12.

  A crankshaft 16 is inserted through the cylinder 11, the separator 13, and the rotor 14. The crankshaft 16 is provided with an axis line substantially parallel to the arrangement direction of the cylinders 11, and the lower end side is inserted into the compression mechanism unit 3. Here, the crankshaft 16 is supported at the upper end side by the drive unit 4 and is driven to rotate about the axis by the drive unit 4. In this embodiment, the drive part 4 is comprised by the electric motor which has a rotor holding the upper end side of the crankshaft 16, and the crankshaft 16 is rotationally driven by rotating this rotor. .

A region of the crankshaft 16 that is inserted into each cylinder 11 is provided with a substantially columnar eccentric shaft portion 17 that engages with the inner peripheral surface of the rotor 14, and the crankshaft 16 is driven to rotate about its axis. Thus, each rotor 14 is rotated eccentrically so as to roll on the cylindrical inner surface 12 of the cylinder 11.
Here, each eccentric shaft portion 17 is provided with its eccentric direction shifted by about 180 ° around the axis of the crankshaft 16 (that is, the phase around the axis is shifted by about 180 °). Thereby, when the crankshaft 16 is rotationally driven, the inertia moment generated in one eccentric shaft portion 17 and the inertia moment generated in the other eccentric shaft portion 17 cancel each other, and the rotation of the crankshaft 16 is stabilized.
Further, end bearings 18 are respectively attached to one end side and the other end side of the rows of the cylinders 11, and the crankshaft 16 is supported by the end bearings 18 so as to be rotatable around the axis.

Hereinafter, each member which comprises the compression mechanism part 3 is demonstrated in detail.
Here, in the present embodiment, the compression mechanism unit 3 is provided with a first cylinder 11a and a second cylinder 11b as the cylinder 11, and the first and second cylinders 11a and 11b are disposed between each other. The separators 13 are sandwiched and arranged in a substantially vertical direction. In the following description, among these cylinders 11, the cylinder 11 disposed above is referred to as a first cylinder 11a, and the cylinder 11 disposed below is referred to as a second cylinder 11b.

As shown in FIG. 2 (AA arrow cross-sectional view in FIG. 1), the first cylinder 11a is a substantially disk-shaped member whose outer diameter is substantially the same as the inner diameter of the cylindrical portion of the housing 2, The cylindrical portion of the housing 2 is fixed so as to be substantially coaxial with the housing 2.
A plurality of through holes opened on the upper and lower surfaces are provided in a radially outer region of the first cylinder 11a, and an upper region and a lower side of the first cylinder 11a in the housing 2 through the through holes. The flow of compressed gas and the like between these regions is allowed.
In the first cylinder 11a, an air passage 21 that opens vertically is provided in a radially inner region.

A through hole 22 that is substantially coaxial with the first cylinder 11a and has a circular cross-sectional view is formed in a radially inner region of the first cylinder 11a. The inner peripheral surface of the through hole 22 constitutes the cylindrical inner surface 12, and the cylindrical rotor 14 is accommodated in the through hole 22. Here, the axial dimension of the rotor 14 is substantially the same as the length of the through hole 22, and the inside of the through hole 22 is surrounded by the rotor 14 by the outer peripheral surface of the rotor 14 and the cylindrical inner surface 12. And a space surrounded by the inner peripheral surface of the rotor 14.
The upper end of the through hole 22 is closed by the end bearing 18, and the lower end is closed by the separator 13.

As will be described later, lubricating oil is supplied between the upper end portion of the rotor 14 and the end bearing 18 and between the lower end portion of the rotor 14 and the separator 13. The gap is sealed with this lubricating oil. Further, the space surrounded by the inner peripheral surface of the rotor 14 is communicated with the inside of the housing 2 through a lubricating oil supply path 37 and the like which will be described later, and the internal pressure of the space surrounded by the inner peripheral surface of the rotor 14 is The internal pressure of the space surrounded by the surface and the cylindrical inner surface 12 is kept higher than the internal pressure.
For this reason, gas leakage from the space surrounded by the outer peripheral surface of the rotor 14 and the cylindrical inner surface 12 to the space surrounded by the inner peripheral surface of the rotor 14 is prevented.

The first cylinder 11 a is formed with an air inlet 23 that communicates from the outer peripheral surface to the cylindrical inner surface 12. A refrigerant pipe P <b> 1 is inserted into the intake port 23, and gas refrigerant of the refrigerant circuit is supplied through the intake port 23 to a space surrounded by the outer peripheral surface of the rotor 14 and the cylindrical inner surface 12 in the through hole 22. It has come to be.
In addition, an exhaust port 24 that connects the cylindrical inner surface 12 and a radially inner area of the upper surface is adjacent to the cylindrical inner surface 12 of the first cylinder 11 a in the circumferential direction with respect to the opening end of the intake port 23. Is formed. Here, although not shown, only the flow of the gas in the exhaust direction from the first cylinder 11a is allowed in the exhaust port 24 or the subsequent stage, and the pressure of the gas supplied to the exhaust port 24 becomes equal to or higher than the target discharge pressure. Only in some cases is a valve allowed to allow gas flow.

Further, the first cylinder 11a is formed with a slit 26 having a substantially equal width from the cylindrical inner surface 12 toward the radially outer side in a region located between the opening end of the intake port 23 and the exhaust port 24 in plan view. ing. The slit 26 is also opened on the upper and lower surfaces of the first cylinder 11a.
Further, in the first cylinder 11 a, a pressure chamber 27 that opens to the top and bottom surfaces and communicates with the inside of the housing 2 is provided at the radially outer end of the slit 26.

A plate-like blade 28 is provided in the slit 26 so as to be substantially parallel to the axis of the first cylinder 11 a and to be advanced and retracted into the through hole 22.
The blade 28 has substantially the same width as the length of the through hole 22 and the same thickness as the slit 26. The blade 28 receives the internal pressure of the pressure chamber 27 (internal pressure of the housing 2) at the end surface facing the pressure chamber 27 side, and is biased by the pressure so as to protrude from the cylindrical inner surface 12 into the through hole 22. Yes. Here, the space between the blade 28 and the inner surface of the slit 26, the space between the blade 28 and the separator 13, and the space between the blade 28 and the end bearing 18 are sealed with the lubricating oil supplied into the first cylinder 11 a. It has come to be.

  In the present embodiment, compressed gas that has been compressed is supplied from the compression mechanism section 3 into the housing 2, and the internal pressure in the pressure chamber 27 communicated with the housing 2 during operation of the rotary compressor 1. Is kept above the internal pressure of each cylinder 11. Accordingly, each blade 28 receives a biasing force directed toward the through hole 22 during operation of the rotary compressor 1.

  The blade 28 is urged toward the inside of the through hole 22 as described above, so that the end portion on the side of the through hole 22 is always brought into contact with the outer peripheral surface of the rotor 14. As a result, the blade 28 advances and retreats in the through hole 22 following the rotor 14 that is eccentrically rotated, and the space surrounded by the outer peripheral surface of the rotor 14 and the cylindrical inner surface 12 is reduced to the low pressure space SL and the high pressure space SH. It is designed to be divided into and. Here, the space between the blade 28 and the outer peripheral surface of the rotor 14 and the space between the rotor 14 and the cylindrical inner surface 12 are sealed by the lubricating oil supplied into the first cylinder 11a, respectively. .

With this configuration, the rotor 14 is eccentrically rotated in a direction (counterclockwise in FIG. 2) that moves from the position facing the slit 26 toward the intake port 23, so that gas can be taken into the cylinder 11 and the cylinder 11. The gas inside is compressed in parallel.
Specifically, when the rotor 14 is eccentrically rotated from a position where the rotor 14 is in contact with only the vicinity of the slit 26 in the cylindrical inner surface 12, a low-pressure space SL is formed in the first cylinder 11a on the intake port 23 side. Is done. Since the capacity of the low-pressure space SL gradually increases as the rotation of the rotor 14 proceeds, gas is taken into the low-pressure space SL from the intake port 23.

  On the other hand, the capacity of the space (high pressure space SH) that was already in the first cylinder 11a gradually decreases with the progress of the rotation of the rotor 14 after the time when the low pressure space SL is formed. Gas compression is performed. When the rotor 14 further rotates and the gas in the high pressure space SH is pressurized to the target discharge pressure, the exhaust port 24 or a valve provided at the subsequent stage is opened, and the gas in the high pressure space SH is exhausted. Exhaust from port 24.

  Further, when the rotor 14 completes one revolution, the gas in the high pressure space SH is completely exhausted, and a new low pressure space SL is formed in the first cylinder 11a. Thereafter, each time the rotor 14 makes one revolution. The above operation is repeated to continuously compress the gas.

  The second cylinder 11b is a substantially disk-shaped member having a configuration similar to that of the first cylinder 11a. The second cylinder 11b includes a ventilation path 21, a through hole 22, an intake port 23, an exhaust port 24, and a slit 26. The pressure chamber 27 is formed in the same arrangement as the first cylinder 11a. Here, although not shown, in the second cylinder 11b, unlike the first cylinder 11a, the exhaust port 24 is configured to connect the cylindrical inner surface 12 and the radially inner region of the lower surface.

  Also in the second cylinder 11b, as in the first cylinder 11a, the rotor 14 is accommodated in the through hole 22, and only the flow of gas in the exhaust direction from the second cylinder 11b is allowed in the exhaust port 24 or subsequent stage. In addition, a valve that allows the gas to flow only when the pressure of the gas supplied to the exhaust port 24 is equal to or higher than the target discharge pressure is provided, and a blade 28 is installed in the slit 26.

A refrigerant pipe P <b> 2 is inserted into the intake port 23, and gas refrigerant of the refrigerant circuit is supplied to the space surrounded by the outer peripheral surface of the rotor 14 and the cylindrical inner surface 12 through the intake port 23. It has become. The through hole 22 of the second cylinder 11 b is closed at the lower end by the end bearing 18 and closed at the upper end by the separator 13.
Here, also in the second cylinder 11b, like the first cylinder 11a, lubricating oil is supplied to the inside, and the members are sealed with the lubricating oil.

  Also in the second cylinder 11b, by rotating the rotor 14 eccentrically, the same operation as the gas compression operation in the first cylinder 11a is performed, and the gas compression is continuously performed.

  As shown in FIG. 1, the separator 13 is a substantially disc-shaped member provided coaxially with respect to the first and second cylinders 11a and 11b. The separator 13 covers the radially inner region of the lower surface of the first cylinder 11a and the radially inner region of the upper surface of the second cylinder 11b in close contact with each other. It is hermetically sealed.

On the radially inner side of the separator 13, an opening 13 a having a circular shape in section view extending from the upper surface to the lower surface is formed coaxially with the separator 13, and the crankshaft 16 is inserted into the opening 13 a. The inner diameter of the opening 13 a is smaller than the eccentric shaft portion 17 of the crankshaft 16.
As shown in FIGS. 1 and 3, the separator 13 is provided with an intermediate bearing 29 that rotatably supports the crankshaft 16 inserted through the opening 13 a. In the present embodiment, the intermediate bearing 29 is a plain bearing having a configuration in which a bearing metal 13b is inserted into the opening 13a.

  Further, the separator 13 is provided with a ventilation path (not shown) that connects the area facing the ventilation path 21 of the first cylinder 11a on the upper surface and the area facing the ventilation path 21 of the second cylinder 11b on the lower surface. Thus, the flow of compressed gas or the like between the lower surface side of the second cylinder 11b and the upper surface side of the first cylinder 11a is allowed through these ventilation paths.

As shown in FIG. 1, end bearings 18 are attached to the upper surface of the first cylinder 11a and the lower surface of the second cylinder 11b, respectively.
The end bearing 18 includes a cylindrical bearing body 31 and a flange 32 provided at an end of the bearing body 31 on the cylinder 11 side and covering a radially inner region of the cylinder 11. The partial bearings 18 are attached to the cylinder 11 so as to be substantially coaxial. In the present embodiment, the end bearing 18 is a plain bearing having a configuration in which a bearing metal 33 is inserted into the bearing body 31.

  The flange 32 covers the periphery of the through-hole 22 in a close contact state in the radially inner region of the cylinder 11, and the flange 32 and the surface of the cylinder 11 are hermetically sealed. On the other hand, at the position facing the exhaust port 24 of the cylinder 11 and the position facing the air passage 21 in the flange 32, air passages (not shown) opened on the upper and lower surfaces of the flange 32 are formed. The air passage 21 communicates with the outside of the flange 32.

  Each end bearing 18 is covered with a dome-shaped muffler 36 in a region opposite to the surface of the flange 32 that is in close contact with the cylinder 11. In the present embodiment, an upper muffler 36a that covers the upper surface of the flange 32 is attached to the upper end bearing 18 attached to the first cylinder 11a. A lower muffler 36b that covers the lower surface of the flange 32 is attached to the lower end bearing 18 attached to the second cylinder 11b.

  The exhaust port 24 of the second cylinder 11b is connected to the space in the lower muffler 36b through the ventilation path of the flange 32 so that compressed gas is sent from the second cylinder 11b. Further, the air passage 21 of the second cylinder 11b is connected to the space in the lower muffler 36b through the air passage of the flange 32, and the compressed gas discharged from the second cylinder 11b is temporarily lowered from the exhaust port 24. After being discharged and separated in the lower muffler 36b, the lubricating oil is separated and then supplied upward through the air passage 21 of the second cylinder 11b. That is, the lower muffler 36b has a role of an oil separator.

On the other hand, the exhaust port 24 of the first cylinder 11a is connected to the space in the upper muffler 36a through the air passage of the flange 32 so that compressed gas is fed from the first cylinder 11a.
Further, the air passage 21 of the first cylinder 11a is connected to the space in the upper muffler 36a through the air passage of the flange 32, and the compressed gas in the lower muffler 36b is connected to the air passage 21 of the second cylinder 11b and the separator. The gas is fed into the upper muffler 36a through the air passage of the heater 13 and the air passage 21 of the first cylinder 11a.
That is, in the compression mechanism unit 3, the compressed gas discharged from the first cylinder 11a and the compressed gas discharged from the second cylinder 11b are merged in the upper muffler 36a.

A gap is provided between the upper muffler 36a and the bearing body 18a of the upper end bearing 18, and the exhaust of the first and second cylinders 11a and 11b merged in the upper muffler 36a through this gap. Is supplied in the housing 2.
The high-pressure compressed gas supplied into the housing 2 in this way is supplied to the downstream side of the refrigerant circuit through the refrigerant pipe P3. The compressed gas is also supplied into the pressure chamber 27 of each cylinder 11, and the pressure is used as the urging force of the blade 28.

  The crankshaft 16 is provided with its lower end positioned in the lubricating oil storage region at the bottom of the housing 2. As shown in FIGS. 1 and 3, the crankshaft 16 is provided with a lubricating oil supply path 37 for supplying lubricating oil from its lower end to each part of the compression mechanism section 3.

In the present embodiment, as shown in FIG. 1, the lubricating oil supply path 37 includes a vertical hole 38 formed along the axis from the lower end to the upper end of the crankshaft 16, and the vertical hole 38 extends from the outer peripheral surface of the crankshaft 16. Of these, a horizontal hole 39 is provided up to a region facing the lubrication target portion.
As a result, the lubricating oil that has entered the vertical hole 38 from the lower end of the crankshaft 16 is raised along the inner peripheral surface of the vertical hole 38 by the centrifugal force generated when the crankshaft 16 is rotationally driven, and each horizontal hole 39. It is sent out of the crankshaft 16 through and supplied to the lubrication target part.

The crankshaft 16 is configured to connect a plurality of units each provided with one eccentric shaft portion 17 that engages with the rotor 14.
In the present embodiment, the crankshaft 16 includes a first unit 16a that configures from the upper end to a portion that is inserted into the opening 13a of the separator 13, and a portion that is inserted into the opening 13a of the separator 13 to the lower end. And a second unit 16b.

  The first unit 16a and the second unit 16b are provided with a connecting portion 41 having a diameter smaller than that of the eccentric shaft portion 17, and the first unit 16a and the second unit 16b include the connecting portion 41 and the opening 13a of the separator. It is connected by this connection part 41 in the state inserted in.

  In the present embodiment, as shown in FIG. 3, the first unit 16 a is provided with an eccentric shaft portion 17 at a position spaced from the lower end, and a portion (lower end portion) below the eccentric shaft portion 17 is The female connecting portion 42 has a smaller diameter than the eccentric shaft portion 17. The female coupling part 42 is formed with a fitting hole 42a opened at the lower end surface along the axis. In addition, the outer peripheral surface of the female connecting portion 42 is received by the bearing metal 13 b of the intermediate portion bearing 29.

On the other hand, the second unit 16b is provided with an eccentric shaft portion 17 at a position spaced from the upper end, and a portion (upper end portion) above the eccentric shaft portion 17 is smaller in diameter than the eccentric shaft portion 17 and female. The male connecting portion 43 is press-fitted into the fitting hole 42 a of the connecting portion 42.
The first unit 16a and the second unit 16b are configured such that the male connecting portion 43 is press-fitted into the fitting hole 42a of the female connecting portion 42 with the female connecting portion 42 inserted into the opening 13a of the separator 13. It is connected by doing.

Further, the first unit 16a is provided with a first horizontal hole 39a that opens to the outer peripheral surface of the portion located directly above the eccentric shaft portion 17, and the first unit 16a slides with the upper end bearing 18 through the first horizontal hole 39a. Lubricating oil is supplied into the moving surface and the first cylinder 11a.
Further, the first unit 16a is provided with a second lateral hole 39b that communicates with the outer peripheral surface of the female connecting portion 42, and an intermediate bearing installed in the opening 13a of the separator 13 through the second lateral hole 39b. Lubricating oil is supplied to the sliding surface with 29.

In the present embodiment, the second lateral hole 29b is opened at the upper part of the outer peripheral surface of the female coupling portion 42 of the first unit 16a, and the lubricating oil is supplied from the upper end side to the sliding surface with the intermediate portion bearing 29. It has come to be.
In this configuration, the lubricating oil supplied to the sliding surface with the intermediate bearing 29 moves downward due to gravity and is also supplied to the lower end side of the sliding surface, so that the entire sliding surface is reliably lubricated. Oil can be supplied.

  Further, the fitting hole 42 a of the female connecting portion 42 is provided up to the upper end of the male connecting portion 43 press-fitted into the fitting hole 42 a, and the inner surface of the fitting hole 42 a and the male connecting portion 43 are provided. A space communicating with the vertical hole 38 is formed between the tip. The second horizontal hole 39b is opened in this space. In this configuration, since the second lateral hole 39b can be formed by processing only the female connecting portion 42, the crankshaft 16 can be easily manufactured.

  In addition, the lubricating oil supplied in the 2nd cylinder 11b is supplied to the sliding surface of the lower end bearing 18 and the 2nd unit 16b.

  As described above, in the rotary compressor 1 configured as described above, the eccentric shaft portions 17 of the crankshaft 16 constituting the compression mechanism portion 3 are provided in the first unit 16a and the second unit 16b, respectively. . The separator 13 is disposed between the first and second units 16 a and 16 b, and the first and second units are inserted in a state where the connecting portion 41 having a smaller diameter than the eccentric shaft portion 17 is inserted into the opening 13 a of the separator 13. By connecting the two units 16 a and 16 b by the connecting portion 41, the crankshaft 16 in which the separator 13 is disposed between the eccentric shaft portions 17 is formed.

That is, in the rotary compressor 1, since it is not necessary to pass the eccentric shaft portion 17 through the opening portion 13a of the separator 13 during assembly, the size of the opening portion 13a can be remarkably reduced. .
Thereby, the eccentric amount of the eccentric shaft part 17 can be made larger than before, and the capacity of the rotary compressor 1 can be increased without increasing the outer shape.

  Further, the rotary compressor 1 is provided with an intermediate bearing 29 for supporting the connecting portion 41 in the opening 13 a of the separator 13, and the crankshaft 16 is also supported in the region between the eccentric shaft portions 17. The crankshaft 16 is less likely to bend during operation of the rotary compressor 1 and has high reliability.

Here, since the connecting portion 41 has a smaller diameter than the eccentric shaft portion 17, the inner diameter of the intermediate bearing 29 is naturally smaller than that of the eccentric shaft portion 17. For this reason, the eccentric shaft part 17 cannot be passed through the intermediate part bearing 29.
In the rotary compressor 1 according to the present embodiment, the connecting portion 41 is inserted into the intermediate bearing 29 provided in the opening 13a of the separator 13, and the first unit 16a and the second unit 16b are connected in this state. Thus, the crankshaft 16 in which the connecting portion 41 is supported by the separator 13 via the intermediate portion bearing 29 can be formed.
That is, this configuration is a novel configuration that can be realized for the first time by adopting a characteristic configuration of the rotary compressor 1 according to the present embodiment in which the crankshaft 16 is configured by a plurality of units.

In the rotary compressor 1, the crankshaft 16 is provided with a lubricating oil supply path 37 for supplying lubricating oil to the sliding surface with the intermediate bearing 29.
That is, the rotary compressor 1 has a lubricating oil supply mechanism that uses a crankshaft, as in a general rotary compressor, so that the configuration can be simplified without greatly changing the configuration from the conventional lubricating oil supply mechanism. With the simple structure, the supply of the lubricating oil to the intermediate bearing 29 can be realized.

  Here, in this embodiment, although the example which provided the female type | mold connection part 42 in the 1st unit 16a and the male type | mold connection part 43 in the 2nd unit 16b was shown, it is not restricted to this, The 1st unit The male connection part 42 may be provided in 16a, and the female connection part 42 may be provided in the second unit 16b.

  Moreover, in this Embodiment, the connection part 41 is comprised by the female type | mold connection part 42 and the male type | mold connection part 43, and these female type | mold connection parts 42 and the male type | mold connection part 43 are fitted, and it is 1st. Although the unit 16a and the second unit 16b are connected to each other, the present invention is not limited to this, and the configuration of the connecting portion 41 can be any other configuration. For example, a technique usually used for connecting members such as bonding, welding, explosive welding, or screw connection between the lower end portion that is the connecting portion 41 of the first unit 16a and the upper end portion that is the connecting portion 41 of the second unit 16b. It is good also as a structure connected by.

  Here, the gap between the intermediate bearing 29 and the connecting portion 41 is very small, and the lubricating oil supplied in the gap spreads along the sliding surface by capillary action. For this reason, in the crankshaft 16, the lateral hole 39b can be opened at an arbitrary position as long as it is a sliding surface with the intermediate bearing 29 or in the vicinity thereof. For example, the position directly above the eccentric shaft portion 17 at the upper end portion of the second unit 16b may be a region that is not press-fitted into the fitting hole 42a, and the horizontal hole 39b may be opened in this region. Further, the first unit 16a and the second unit 16b have a horizontal hole 39b that penetrates both the male connecting part 43 and the female connecting part 42 from the vertical hole 38 of the second unit 16b and reaches the outer peripheral surface of the female connecting part 42. It is good also as a structure provided.

  In this embodiment, an example in which the rotary compressor 1 is a vertical rotary compressor has been described. However, the present invention is not limited to this, and a horizontal rotary compressor may be used. In this case, the lubricating oil is supplied to each part using a pump or the like.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS.
As shown in the longitudinal sectional view of FIG. 4, the rotary compressor 51 according to this embodiment is a partial configuration of the compression mechanism unit 3 instead of the compression mechanism unit 3 in the rotary compressor 1 shown in the first embodiment. The main feature is that the compression mechanism unit 53 in which the above is changed is used.
Below, the same code | symbol is shown about the same or same structure as the rotary compressor 1 shown in 1st embodiment, and detailed description is abbreviate | omitted.

The compression mechanism portion 53 is mainly characterized in that, in the compression mechanism portion 3 shown in the first embodiment, the second unit 16b of the crankshaft 16 is made of a material that is lighter than the material of the first unit 16a. is there.
In the present embodiment, the first unit 16a to which the driving force from the driving unit 4 is input is made of iron having excellent strength, and sufficient durability and reliability are ensured, and the first unit 16a has a smaller load than the first unit 16a. The two units 16b are made of aluminum or aluminum base alloy which is lighter than iron.

And in this compression mechanism part 53, as shown to FIG. 5 (BB arrow sectional drawing of FIG. 4) and FIG. 6 (CC arrow sectional drawing of FIG. 4), the eccentric shaft of the 2nd unit 16b. The eccentric amount EC ₂ (see FIG. 6) of the portion 17 is set larger than the eccentric amount EC ₁ (see FIG. 5) of the eccentric shaft portion 17 of the first unit 16a. Here, the eccentricity EC ₂ of the second unit 16b is the moment of inertia of the first unit 16a and the second unit 16b is set to be the same level. Further, the outer diameter of the rotor 14 (hereinafter referred to as the rotor 14a) with which the eccentric shaft portion 17 is engaged is reduced by increasing the amount of eccentricity of the eccentric shaft portion 17 of the second unit 16b.
By adopting these configurations, the capacity of the second cylinder 11b is further increased than the capacity of the first cylinder 11a.

The rotary compressor 51, since the second unit 16b as described above is formed by the material of the lighter than the first unit 16a, the eccentricity EC ₂ of the eccentric shaft portion 17 of the second unit 16b first unit be larger than the eccentricity EC ₁ of the eccentric shaft portion 17 of the 16a, it is possible to keep the moment of inertia of the first unit 16a and the second unit 16b to the same degree.
Thereby, the capacity of the second cylinder 11b on the lower end side is further increased from the capacity of the first cylinder 11a on the upper end side while maintaining a good balance of the moment of inertia when the crankshaft 16 is rotationally driven. Large capacity can be achieved.

Further, as shown in FIG. 4, the compression mechanism portion 53 of the rotary compressor 51 has a configuration in which the separator 63 according to this embodiment is used instead of the separator 13 in the compression mechanism portion 3 shown in the first embodiment. ing.
Moreover, in this compression mechanism part 53, as shown in FIG.4 and FIG.6, the exhaust port 24 of the 2nd cylinder 11b is the radial direction of the cylindrical inner surface 12 and an upper surface similarly to the exhaust port 24 of the 1st cylinder 11a. It is set as the structure which connects an inner area | region.

  As shown in FIG. 4 and FIG. 7 (cross-sectional view taken along the line DD in FIG. 4), the separator 63 receives compressed gas discharged from the second cylinder 11b as compressed gas in the rotary compressor 51. A discharge path 66 that leads to the downstream side (inside the air passage 21 of the first cylinder 11a) is provided. The separator 63 is not provided with the ventilation path provided by the separator 13.

Further, as shown in FIG. 8 (a cross-sectional view taken along the line E-E in FIG. 4), the flange 32 of the upper end bearing 18 is located at a position facing the exhaust port 24 of the first cylinder 11 a from the lower surface to the upper surface. A first air passage 32a is formed to communicate with the first air passage 32a. Further, a second air passage 32b that extends from the lower surface to the upper surface is formed at a position of the flange 32 that faces the air passage 21 of the first cylinder 11a. By the first air passage 32a and the second air passage 32b, the exhaust of the first cylinder 11a and the exhaust of the second cylinder 11b are joined in the space in the upper muffler 36a.
Here, in this compression mechanism part 53, as shown in FIG. 4, instead of the lower end bearing 18, a flat end bearing 68 is used. The end bearing 68 is not provided with the air passage provided by the end bearing 18.

  The discharge path 66 includes a vertical portion 66 a (see FIGS. 4 and 8) provided substantially vertically from a region facing the exhaust port 24 of the second cylinder 11 b to the upper surface on the lower surface of the separator 63, and a vertical portion on the upper surface of the separator 63. A horizontal portion 66b (see FIG. 7) extending from the upper end of 66a to a region facing the opening of the air passage 21 on the lower surface of the first cylinder 11a.

As shown in FIG. 4, the vertical portion 66a is provided with a reduced diameter portion 66c in the vicinity of the lower end. In the vertical portion 66a, a valve body 67a that closes the reduced diameter portion 66b is provided above the reduced diameter portion 66c so as to be movable in a substantially vertical direction.
In the vertical portion 66a, an urging member 67b for urging the valve body 67a downward is disposed above the valve body 67a. In the present embodiment, a coil spring is used as the urging member 67b.
With this configuration, the reduced diameter portion 66c is opened by the valve body 67a being pushed up against the urging force of the urging member 67b by the pressure of the exhaust gas supplied from the exhaust port 24 of the second cylinder 11b into the vertical portion 66a. Thus, passage of exhaust gas through the ventilation path 66 is allowed. Further, in a state where the internal pressure in the vertical portion 66a is lower than the urging force of the urging member 67b (that is, a state in which compressed gas is not discharged from the second cylinder 11b), the valve element 67a is urged by the urging force of the urging member 67b. Is pressed against the reduced diameter portion 66c to close it, and the backflow of compressed gas from the discharge path 66 to the second cylinder 11b is prevented.

Further, the valve body 67a also serves as a float valve, and buoyancy is generated and lifted upward when a predetermined amount or more of lubricating oil is stored in the vertical portion 66a. The valve body 67a is lifted by buoyancy in this way, so that the lubricating oil in the vertical portion 66a falls into the second cylinder 11b through the reduced diameter portion 66b by gravity.
That is, the vertical portion 66a and the valve body 67a constitute an oil separator 67 that separates the lubricating oil from the compressed gas sent into the discharge path 66 and returns it to the second cylinder 11b.

  Thus, in this rotary compressor 51, since the separator 63 has the oil separator 67, the lower muffler 36b can be omitted, and the dimension of the compression mechanism unit 4 in the height direction can be reduced. Miniaturization is possible.

  Here, in the present embodiment, an example in which the valve body 67a and the urging member 67b are provided in the discharge path 66 and these members are used as a check valve or an oil separator is shown. For example, a check valve or an oil separator may be configured by other configurations, such as a rotary compressor 71 shown in the longitudinal sectional view of FIG. 9.

The rotary compressor 71 is mainly characterized in that a separator 73 is provided instead of the separator 63 in the rotary compressor 51 shown in the second embodiment.
In the separator 63, the upper end of the vertical portion 66 a is closed in the horizontal portion 66 b instead of providing the valve body 67 a, the biasing member 67 b, and the reduced diameter portion 66 c in the vertical portion 66 a of the discharge path 66. A leaf valve 76 is provided.

The leaf valve 76 is a plate-like elastic body having one end disposed at a position covering the upper end of the vertical portion 66a and the other end fixed to the bottom surface of the horizontal portion 66b. One end of the leaf valve 76 is pressed against the upper end of the vertical portion 66a by its elastic force to close the vertical portion 66a, and the pressure of the exhaust gas supplied into the vertical portion 66a from the exhaust port 24 of the second cylinder 11b. When the one end is pushed up, the vertical portion 66a is opened, and the passage of the exhaust gas through the ventilation path 66 is allowed.
Further, in a state where the internal pressure in the vertical portion 66a is lower than the elastic force of the leaf valve 76 (that is, a state where compressed gas is not discharged from the second cylinder 11b), one end of the vertical portion 66a is a vertical portion due to the elastic force of the leaf valve 76. It is pressed against the upper end of 66a to close it, and the backflow of compressed gas from the discharge path 66 to the second cylinder 11b is prevented.

  Here, the peripheral edge 66d at the upper end of the vertical portion 66a on the bottom surface of the horizontal portion 66b is provided so as to protrude upward from the other regions, and at least one end side portion of the leaf valve 76 is formed on the horizontal portion 66b. It is spaced apart from other parts of the bottom surface.

The leaf valve 76 also serves as a float valve. When a predetermined amount or more of lubricating oil is stored in the horizontal portion 66b, buoyancy is generated and one end is lifted upward. Thus, one end is lifted by buoyancy, so that the lubricating oil in the horizontal portion 66b falls into the second cylinder 11b through the vertical portion 66a by gravity.
That is, in this rotary compressor 71, the horizontal portion 66b and the leaf valve 76 constitute an oil separator 77 that separates the lubricating oil from the compressed gas sent into the discharge passage 66 and returns it to the second cylinder 11b. .

[Third embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
As shown in the longitudinal sectional view of FIG. 10, the rotary compressor 81 according to the present embodiment is a partial configuration of the compression mechanism unit 3 instead of the compression mechanism unit 53 in the rotary compressor 51 shown in the second embodiment. The main feature is the use of a compression mechanism 83 in which is changed.
In the following, the same or the same configuration as that of the rotary compressor 51 shown in the second embodiment is denoted by the same reference numeral, and detailed description thereof is omitted.

In the compression mechanism portion 53 shown in the second embodiment, the compression mechanism portion 83 is provided with a third cylinder 11c having a cylindrical inner surface 12 coaxially between the first cylinder 11a and the upper end bearing 18, A second separator 93 is provided between the three cylinders 11c and the first cylinder 11a. Here, the third cylinder 11c has substantially the same configuration as the first cylinder 11a, and the rotor 14 is accommodated in the third cylinder 11c in the same manner as the first cylinder 11a.
Further, the second separator 93 has substantially the same configuration as the separator 63.

In the compression mechanism 83, a crankshaft 86 is provided instead of the crankshaft 16.
Instead of the first unit 16a, the crankshaft 86 has an upper part held by the drive unit 4 and a lower part inserted into the third cylinder 11c and the rotor 14 in the third cylinder 11c. And a fourth unit 16d provided between the third unit 16c and the second unit 16b and inserted through the rotor 14 in the first cylinder 11a.

The third unit 16c has substantially the same configuration as the first unit 16a, and the fourth unit 16d has a configuration in which a female connecting portion 42 is provided below the eccentric shaft portion 17 in the second unit 16b. ing.
The third unit 16c and the fourth unit 16d are configured so that the female connection part 42 and the male connection part 43 are inserted into the opening of the second separator 93 while the female connection part 42 and the male connection part 43 are inserted into each other. It is connected by fitting the part 43. The separator 93 is provided with an intermediate bearing 29 that rotatably supports the crankshaft 16 inserted through the opening 13a.

Similarly, the fourth unit 16d and the second unit 16b are configured such that the female connection part 42 and the male unit 42 are connected to each other in a state where the female connection part 42 and the male connection part 43 are inserted into the opening of the separator 63. It is connected by fitting the connecting portion 43.
Further, the third unit 16c and the fourth unit 16d are respectively provided with a vertical hole 38 and a horizontal hole 39 of the lubricating oil supply path 37, through which the lubricating oil is introduced into the third cylinder 11c and the first cylinder 11a. It comes to be supplied.
The second, third, and fourth units 16b, 16c, and 16d are connected in a state in which the eccentric direction of each eccentric shaft portion 17 is shifted by about 120 ° around the axis of the crankshaft 86, The balance of the moment of inertia around the axis of the crankshaft 86 is maintained.

Hereinafter, the configuration of each part of the compression mechanism 83 will be described in detail.
In the separator 63 shown in the second embodiment, the second separator 93 is provided with the horizontal portion 66b of the discharge path 66 up to a region facing the air passage 21 opened on the lower surface of the third cylinder 11c, and further the first cylinder 11a. The second discharge path (not shown) that leads from the region facing the exhaust port 24 to the inside of the horizontal portion 66b is provided.
That is, the compression mechanism 83 is configured such that the exhaust of the first cylinder 11a and the exhaust of the second cylinder 11b merge in the discharge path 66 (not shown in FIG. 10) of the second separator 83.

The third cylinder 11c has a configuration in which the intake port 23 is eliminated from the first cylinder 11a, and the upper end of the air passage 21 is opened in a region where the intake port 23 is opened in the cylindrical inner surface 12 instead of the upper surface. ing.
The ventilation path 21 of the third cylinder 11 c is connected to the exhaust port 24 of the first cylinder 11 a by the discharge path 66 of the second separator 93. The vent path 21 of the third cylinder 11c is connected to the exhaust port 24 of the second cylinder 11b by the discharge path 66 and the second discharge path. That is, the third cylinder 11c is connected in series to the first and second cylinders 11a and 11b on the gas flow path in the compression mechanism 83.

  Here, the exhaust port 24 of the third cylinder 11c is supplied into the upper muffler 39a through the ventilation path of the flange 32 of the upper end bearing 18, and after being supplied into the housing 2 from the upper muffler 39a, the refrigerant pipe It is sent to the downstream side of the refrigerant circuit through P3.

In this compression mechanism 83, the crankshaft 86 is rotationally driven around the axis by the drive unit 4, whereby the rotor 14 is eccentrically rotated in the third cylinder 11c, and the first cylinder 11a and the second cylinder 11b It is set as the structure by which the further compression of the supplied compressed gas is performed.
That is, the compression mechanism 83 is configured to perform multistage compression by a plurality of cylinders 11 connected in series.

  For this reason, since the compression ratio of the gas in each of the cylinders 11 connected in series is smaller than that of a rotary compressor configured to obtain compressed gas having a final discharge pressure by one-stage compression, rotary compression of one-stage compression Compared with the machine, the pressure difference between the low pressure space SL and the high pressure side space SH in the space partitioned by the rotor 14 and the blades 28 in each cylinder 11 may be small.

  Thus, since the pressure difference between the low pressure space SL and the high pressure side space SH in each cylinder 11 is small, in this rotary compressor 81, the high pressure side space SH in the cylinder 11 is transferred from the low pressure side space SL to the low pressure side space SL. Compressed gas leakage is reduced and operating efficiency is high. This configuration is particularly effective when used for compression of a refrigerant that requires high compression (for example, a natural refrigerant such as a carbon dioxide refrigerant or an ammonia refrigerant).

  In this rotary compressor 81, the capacity of the second cylinder 11b can be different from that of the third cylinder 11c, and the compression ratio can be changed between the second cylinder 11b and the third cylinder 11c. More detailed compression conditions can be set according to the nature of the gas to be compressed.

[Fourth embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG.
As shown in the longitudinal sectional view of FIG. 11, the rotary compressor 101 according to this embodiment is a partial configuration of the compression mechanism unit 3 instead of the compression mechanism unit 3 in the rotary compressor 1 shown in the first embodiment. Is used, and the housing 2 includes a lower side region (hereinafter referred to as a first region S1) in which the compression mechanism unit 103 is provided and an upper side in which the drive unit 4 is provided. A main partition wall 106 is provided to partition into a region (hereinafter referred to as a second region S2).
Below, the same code | symbol is shown about the same or same structure as the rotary compressor 1 shown in 1st embodiment, and detailed description is abbreviate | omitted.

  In the rotary compressor 101, a refrigerant pipe P4 is inserted into the housing 2 from the outside as a refrigerant pipe connecting the rotary compressor 101 and the refrigerant circuit, instead of the refrigerant pipes P1 to P3. The refrigerant of the refrigerant circuit is supplied to the second region S2 of the housing 2 through the refrigerant pipe P4.

In addition, a refrigerant pipe P5 that connects the inside of the second region S2 and the compression mechanism 103 in the first region S1 is inserted in the side surface of the housing 2, and the gas refrigerant supplied into the second region S2 The refrigerant is sent into the compression mechanism 103 through the refrigerant pipe P5.
That is, the second region S <b> 2 is a passage through which the gaseous refrigerant supplied to the rotary compressor 101 passes before being sent into the compression mechanism unit 103.

  The compression mechanism unit 103 compresses the gaseous refrigerant supplied through the refrigerant pipe P5 to form a high-pressure compressed gas, and then sends the compressed gas into the first region S1 of the housing 2. That is, during the operation of the rotary compressor 101, the internal pressure in the first region S <b> 1 in which the compression mechanism unit 103 is accommodated is kept higher than the internal pressure of each cylinder 11. Thereby, the operation of the blade 28 in each cylinder 11 and the supply of the lubricating oil in each cylinder 11 are performed satisfactorily.

  A refrigerant pipe P6 is inserted into the lower side surface of the housing 2 from the outside, and the compressed gas temporarily stored in the first region S1 of the housing 2 is sent to the downstream side of the refrigerant circuit through the refrigerant pipe P6. It is supposed to be.

Hereinafter, a detailed configuration of the compression mechanism unit 103 will be described.
The compression mechanism section 103 is the same as the compression mechanism section 3 shown in the first embodiment, the ventilation path 21 of the first and second cylinders 11a and 11b, the ventilation path of the separator 13, and the ventilation path provided in the lower end bearing 18. Of these, the air passage connected to the air passage 21 of the second cylinder 11b and the upper muffler 36a are eliminated.
On the other hand, a refrigerant pipe P5 is inserted into the intake port 23 of the second cylinder 11b, and a gaseous refrigerant to be compressed is supplied into the second cylinder 11b through the refrigerant pipe P5.

The compression mechanism 103 is provided with a refrigerant pipe P7 that communicates from the inside of the lower muffler 36b to the intake port 23 of the first cylinder 11a, and the exhaust of the second cylinder 11b passes through the lower muffler 36b and the refrigerant pipe P7. It is supplied into one cylinder 11a. Then, the gaseous refrigerant that has undergone the second compression in the first cylinder 11a is discharged into the first space S1 through the exhaust port 24 of the first cylinder 11a and the air passage of the upper end bearing 18, and temporarily. And then sent to the downstream side of the refrigerant circuit through the refrigerant pipe P6.
Moreover, in this rotary compressor 101, since 1st area | region S1 acts as an oil separator, lubricating oil can be collect | recovered from the compressed gas to discharge.

In the rotary compressor 101 configured as described above, the second region S2 in which the drive unit 4 is installed in the housing 2 and the first region S1 in which the compression mechanism unit 103 is provided are partitioned by a main partition wall 106, The second region S <b> 2 takes in the gas to be compressed before being compressed by the compression mechanism unit 103, that is, the coldest gas in the rotary compressor 101.
For this reason, in this rotary compressor 101, the drive unit 4 is isolated from the high-temperature compressed gas pressurized by the compression mechanism unit 104, and the drive unit 4 is cooled by the coldest gas. It is difficult to cause damage to the drive unit 4 due to the high reliability and long life.

  Further, in the rotary compressor 101, the housing 2 is partitioned into the first region S1 and the second region S2, and the compressed gas compressed by the compression mechanism 103 is stored only in the first region S1. . For this reason, in this rotary compressor 101, only the portion of the housing 2 that constitutes the first region S1 needs to have sufficient strength to withstand the final discharge pressure, so that the manufacturing cost can be reduced. .

[Fifth embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIGS.
As shown in the longitudinal sectional view of FIG. 12, the rotary compressor 111 according to this embodiment is a partial configuration of the compression mechanism unit 3 instead of the compression mechanism unit 103 in the rotary compressor 101 shown in the fourth embodiment. It is assumed that the compression mechanism unit 113 is used.
In the following, the same or the same configuration as that of the rotary compressor 101 shown in the fourth embodiment is indicated by the same reference numeral, and detailed description thereof is omitted.

The compression mechanism unit 113 includes a front-stage compression mechanism unit 113a that has substantially the same configuration as the compression mechanism unit 3, and a rear-stage compression mechanism unit 113b that further compresses the compressed gas compressed by the front-stage compression mechanism unit 113a. Yes.
The housing 2 is provided with a cylinder partition wall 116 that divides the first region S1 into a high pressure region H and a low pressure region L in which the rear-stage compression mechanism 113b is accommodated. As will be described later, the cylinder partition wall 116 also serves as a separator that partitions the space in the fourth cylinder 11d and the space in the first cylinder 11a.

  The pre-stage compression mechanism portion 113 a is configured such that, in the compression mechanism portion 3, the upper surface of the first cylinder 11 a is covered with a cylinder partition wall 116 instead of the upper end bearing 18. Further, a crankshaft 126 described later is inserted into the first and second cylinders 16a and 16b instead of the crankshaft 16.

In the first cylinder 11a and the second cylinder 11b, the refrigerant pipe P5 is inserted into the intake port 23, respectively, so that the gaseous refrigerant in the second region S2 is supplied.
Further, the exhaust from the first cylinder 11a and the second cylinder 11b is discharged into the low pressure region L and temporarily stored. That is, during the operation of the rotary compressor 111, the internal pressure in the low pressure region L in which the pre-stage compression mechanism 113a is accommodated is maintained at or above the internal pressure of the first and second cylinders 11a and 11b. Thereby, the operation of the blade 28 in the first and second cylinders 11a and 11b, the supply of the lubricating oil to the respective parts in the first and second cylinders 11a and 11b, and the sealing of the respective parts by the lubricating oil are performed satisfactorily. It has come to be.

The rear-stage compression mechanism 113b includes a fourth cylinder 11d configured substantially the same as the first cylinder 11a, and a rotor 14 and a blade 28 (not shown in FIG. 12) housed in the fourth cylinder 11d. doing.
Here, the upper surface of the fourth cylinder 11 d is covered by the upper end bearing 18, and the lower surface of the fourth cylinder 11 d is covered by the cylinder partition wall 116.
The intake port 23 of the fourth cylinder 11d communicates with the low pressure region L through a ventilation passage provided in the cylinder partition wall 116, so that the compressed gas in the low pressure region L is sent into the fourth cylinder 11d. It has become. At this time, part of the lubricating oil supplied into the first cylinder 11a and the second cylinder 11b is also sent into the fourth cylinder 11d together with the compressed gas.

  The high-pressure compressed gas compressed by the fourth cylinder 11d is discharged into the high-pressure region H through the air passage of the upper end bearing 18 and temporarily stored. That is, during the operation of the rotary compressor 111, the internal pressure in the high pressure region H in which the rear-stage compression mechanism 113b is accommodated is maintained at or above the internal pressure of the fourth cylinder 11d. Thereby, the operation of the blade 28 in the fourth cylinder 11d, the supply of the lubricating oil to each part in the fourth cylinder 11d, and the sealing of each part by the lubricating oil are performed satisfactorily.

A cylinder partition wall 116 provided between the front-stage compression mechanism 113a and the rear-stage compression mechanism 113b is provided on a lower plate 117 that covers the upper surface of the first cylinder 11a, and on the upper side of the lower plate 117. An upper plate 118 that covers the lower surface, and a connecting portion 119 that connects the upper surface of the lower plate 117 and the lower surface of the upper plate 118 to partition the high pressure region H and the low pressure region L together with the upper and lower plates 117 and 118. Yes.
The lower plate 117 is provided with a ventilation path that connects the exhaust port 24 of the first cylinder 11a and the low pressure region L.

Here, the lower plate 117 and the upper plate 118 are arranged with their horizontal positions shifted, a part of the upper surface of the lower plate 117 is exposed to the high pressure region H, and a part of the lower surface of the upper plate 118 is low pressure. The region L is exposed. As a result, an oil sump 121 surrounded by the upper surface of the lower plate 117, the connecting portion 119 and the inner surface of the casing 2 is formed in the high pressure region H below the upper plate 118.
The oil sump 121 stores lubricating oil used for lubrication and sealing of each part of the rear-stage compression mechanism 113b.

  Further, the rotary compressor 111 is provided with an oil return 121 a for sending the lubricating oil in the oil sump 121 to the low pressure region L of the housing 2. The oil return 121a is constituted by a pipe provided with an electromagnetic valve or a capillary.

When the oil return 121a is constituted by a pipe provided with a solenoid valve, the solenoid valve is opened and the lubricant oil is sent to the low pressure region L when a predetermined amount or more of lubricant oil is stored in the oil sump 121. It is supposed to be configured.
Further, when the oil return 121a is constituted by a capillary, the amount of the lubricating oil fed into the low pressure region L through the capillary within the unit time is substantially the same as the lubricating oil fed together with the compressed gas from the low pressure region L per unit time. A capillary having an appropriate resistance is used.

  Further, the cylinder partition wall 116 is formed with a through hole 122 through which the crankshaft 126 is inserted through the lower plate 117, the upper plate 118, and the connection portion 119. Further, the connecting portion 119 is provided with a horizontal hole 123 that extends from the region where the lubricating oil is stored in the oil reservoir 121 to the through hole 122, and the lubricating oil in the oil reservoir 121 passes through the lateral hole 123 to the crankshaft 126. It comes to be supplied.

As described above, the crankshaft 126 is inserted through the front-stage compression mechanism 113a and the rear-stage compression mechanism 113b.
Like the crankshaft 16, the crankshaft 126 is formed by connecting a plurality of units each provided with one eccentric shaft portion 17 each.

  Specifically, the crankshaft 126 has an upper portion held by the drive unit 4 and a lower portion inserted through the rear compression mechanism portion 113b and the through hole 122 of the cylinder partition wall 116, and the through hole of the cylinder partition wall 115. 122 inserted into the opening 13a of the separator 13 of the pre-stage compression mechanism 113a and the second unit 126b constituting the portion inserted into the opening 13a of the separator 13 of the pre-stage compression mechanism 113a. And a third unit 126c that configures the portion from the bottom to the lower end.

The lower end of the first unit 126a, the upper and lower ends of the second unit 126b, and the upper end of the third unit 126c are each provided with a connecting portion having a smaller diameter than the eccentric shaft portion 17.
And the 1st unit 126a and the 2nd unit 126b are connected by these connection parts in the state which penetrated the connection part provided in each to the through-hole 122 provided in the cylinder partition 116. In addition, the second unit 126b and the third unit 126c are connected by these connecting portions in a state where the connecting portions provided in the second unit 126b and the third unit 126c are inserted into the openings provided in the separator 13, respectively.

  The first, second, and third units 126a, 126b, and 126c are connected in a state where the eccentric directions of the eccentric shaft portions 17 are shifted by about 120 ° around the axis of the crankshaft 126. The balance of the moment of inertia around the axis of is maintained.

  As shown in FIGS. 12 and 13, the crankshaft 126 is provided with a first lubricating oil supply path 127 in the first unit 126a. As shown in FIG. 13, the first lubricating oil supply path 127 includes a first horizontal hole 127a that leads to a region facing the horizontal hole 123 of the connection portion 119 in the first unit 126a, and an upper portion along the axis from the first horizontal hole 127a. And a second horizontal hole 127c provided from the vertical hole 127b to a region facing the lubrication target portion of the outer peripheral surface of the crankshaft 126.

  In the first lubricating oil supply path 127, the lubricating oil in the oil sump 121 is supplied into the vertical hole 127b through the first horizontal hole 127a. Thus, the lubricating oil supplied into the vertical hole 127b is raised along the inner peripheral surface of the vertical hole 127b by the centrifugal force generated by rotating the crankshaft 126, and also through the second horizontal hole 128c. It is sent out and supplied to the lubrication target site.

Further, a second lubricating oil supply path 128 is provided in a region constituted by the second unit 126b and the third unit 126c in the crankshaft 126.
The second lubricating oil supply path 128 includes a vertical hole 128a formed along the axis from the lower end of the third unit 126c to the vicinity of the upper end of the second unit 126b, and a vertical hole 128a in each of the second unit 126b and the third unit 126c. There is a lateral hole 128b provided from the inner peripheral surface to the region facing the lubrication target portion on the outer peripheral surface.

  As a result, the lubricating oil that has entered the vertical hole 128a from the lower end of the crankshaft 126 is raised along the inner peripheral surface of the vertical hole 128a by the centrifugal force generated by rotationally driving the crankshaft 126, and each horizontal hole 128b. Is sent out of the crankshaft 126 and supplied to the lubrication target site.

  Such a configuration in which two independent lubricating oil supply paths are provided on one crankshaft is difficult to realize when the crankshaft is configured by a single member. This is a configuration that can be easily realized only when the shaft 126 is composed of a plurality of units. That is, in this embodiment, the crankshaft 126 having the first lubricating oil supply path 127 and the second lubricating oil supply path 128 can be easily made by processing each of the first to third units 126a to 126c. Can be manufactured.

  For example, as shown in FIG. 13, the vertical hole 127b of the crankshaft 126 has a fitting hole 42a formed at the lower end of the first unit 126a, and the male hole formed at the upper end of the second unit 126b in the fitting hole 42a. It can be formed by press-fitting the mold connecting portion 43 and closing the lower end of the fitting hole 42a.

  According to the rotary compressor 111 configured as described above, the first mechanism S1 in which the compression mechanism unit 113 is arranged is divided into the high-pressure side region H and the low-pressure side region L, and the compression mechanism unit 113 has a high pressure. Since the lubricating oil can be satisfactorily supplied to each of the side region H and the low pressure side region L, the performance is high and the life is also long.

[Sixth embodiment]
Next, a sixth embodiment of the present invention will be described with reference to FIG.
As shown in the longitudinal sectional view of FIG. 14, the rotary compressor 131 according to the present embodiment is a partial configuration of the compression mechanism portion 113 instead of the compression mechanism portion 113 in the rotary compressor 111 shown in the fifth embodiment. The main feature is that the compression mechanism unit 133 is used.
In the following, the same or the same configuration as that of the rotary compressor 111 shown in the fifth embodiment is denoted by the same reference numeral, and detailed description thereof is omitted.

  The compression mechanism unit 133 is configured such that, in the compression mechanism unit 113, the rear-stage compression mechanism unit 113b is disposed adjacently below the front-stage compression mechanism unit 113a, and the rear-stage compression mechanism unit 113b is accommodated in the first region S1. A cylinder partition wall 136 according to the present embodiment is used as a cylinder partition wall that partitions the high pressure region H and the low pressure region L. As will be described later, the cylinder partition wall 136 also serves as a separator that partitions the space in the second cylinder 11b and the space in the fifth cylinder 11e.

  Further, the upper surface of the first cylinder 11a constituting the front-stage compression mechanism portion 113a is covered by the upper end bearing 18, and the lower surface of the second cylinder 11b constituting the front-stage compression mechanism portion 113a is covered by the cylinder partition wall 136. ing. Instead of the crankshaft 126, a crankshaft 146 described later is inserted into the first and second cylinders 16a and 16b. Here, in the present embodiment, the upper muffler 36a and the refrigerant pipe P5 are not provided.

In this rotary compressor 131, the pre-stage compression mechanism 113a is disposed adjacent to the lower side of the main partition wall 106, and the intake port 23 of the first cylinder 11a and the intake port 23 of the second cylinder 11b do not go through the refrigerant pipe P5. In addition, it is directly connected to the second region S2, and the gas refrigerant is directly supplied from the second region S2.
Further, the exhaust from the first cylinder 11a and the second cylinder 11b is discharged into the low pressure region L and temporarily stored.

The rear-stage compression mechanism 113b has a fifth cylinder 11e having substantially the same configuration as the second cylinder 11b. Specifically, the fifth cylinder 11e is configured such that the exhaust port 24 is opened on the lower surface and exhausts downward through the air passage of the lower end bearing 18.
In the rear-stage compression mechanism 113b, the upper surface of the fifth cylinder 11e is covered with a cylinder partition wall 136, and the lower surface of the fifth cylinder 11e is covered with the lower end bearing 18.

The fifth cylinder 11e has an intake port 23 communicated with the low pressure region L through a vent path provided in a pipe 136a penetrating the cylinder partition wall 136 so that the compressed gas in the low pressure region L is transferred to the fifth cylinder 11e. 11e.
The high-pressure compressed gas compressed by the fifth cylinder 11e is once discharged into the lower muffler 36b through the ventilation passage of the lower end bearing 18, and after the lubricating oil is removed, the high-pressure region passes through the lower muffler 36b. It is discharged into H and temporarily stored.

  A cylinder partition wall 136 provided between the front-stage compression mechanism portion 113a and the rear-stage compression mechanism portion 113b covers a lower plate 137 that covers the upper surface of the fifth cylinder 11e and partitions the high-pressure region H and the low-pressure region L, and the lower plate 137. And the upper plate 138 covering the lower surface of the second cylinder 11b, the upper surface of the lower plate 137, and the lower surface of the upper plate 138 are connected so that the upper and lower plates 137, 138 are spaced apart from each other. And a connection portion 139 to be connected.

Here, since the lower plate 137 and the upper plate 138 are separated from each other in this manner, an oil sump 141 is formed between them.
This oil sump 141 stores lubricating oil used for lubrication and sealing of each part of the pre-stage compression mechanism 113a.
The pipe 136a provided in the cylinder partition wall 136 has an upper end provided above the oil storage area of the oil sump 141, so that only the compressed gas in the low pressure area L is fed into the downstream compression mechanism 113b. It has become.

  Further, the cylinder partition wall 136 is formed with a through hole 142 through which the crankshaft 146 is inserted through the lower plate 137, the upper plate 138, and the connecting portion 139. Further, the connecting portion 139 is provided with a horizontal hole 143 that leads from the region where the lubricating oil is stored in the oil reservoir 141 to the through hole 142, and the lubricating oil in the oil reservoir 141 is supplied to the crankshaft 146 through the horizontal hole 143. It comes to be supplied.

As described above, the crankshaft 146 is inserted through the front-stage compression mechanism 113a and the rear-stage compression mechanism 113b.
Like the crankshaft 16, the crankshaft 146 is formed by connecting a plurality of units each having one eccentric shaft portion 17 provided.

  Specifically, the crankshaft 146 includes a first unit 146a having an upper portion held by the drive unit 4 and a lower portion inserted into the opening 13a of the separator 13 of the front-stage compression mechanism portion 113a. The compression mechanism 113a is inserted into the second unit 146b that constitutes from the portion inserted into the opening 13a of the separator 13 to the portion inserted into the through hole 142 of the cylinder partition wall 136, and the through hole 12 of the cylinder partition wall 136. And a third unit 146c that configures from the part to the lower end.

The lower end of the first unit 146a, the upper and lower ends of the second unit 146b, and the upper end of the third unit 146c are each provided with a connecting portion having a smaller diameter than the eccentric shaft portion 17.
And the 1st unit 146a and the 2nd unit 146b are connected by these connection parts in the state which penetrated the connection part provided in each to the opening part 13a of the separator 13. As shown in FIG. The second unit 146b and the third unit 146c are connected by these connecting portions in a state where the connecting portions provided in the second unit 146b and the third unit 146c are inserted into the through holes 142 of the cylinder partition wall 136, respectively.

  The crankshaft 146 is provided with a first lubricating oil supply path 147 in the first unit 146a and the second unit 146b. The first lubricating oil supply path 147 includes a first horizontal hole 147a that communicates with a region facing the lateral hole 143 of the connecting portion 139 in the second unit 146a, and a vertical hole 147b that communicates from the first lateral hole 147a along the axis to the first unit 146a. The first unit 146a and the second unit 146b have a second lateral hole (not shown) provided from the vertical hole 147b to a region facing the lubrication target portion of the outer peripheral surface of the crankshaft 126.

  In the first lubricating oil supply path 147, the lubricating oil in the oil sump 141 is supplied into the vertical hole 147b through the first horizontal hole 147a. The lubricating oil thus supplied into the vertical hole 147b is raised along the inner peripheral surface of the vertical hole 147b by the centrifugal force generated when the crankshaft 16 is rotationally driven, and also outside the crankshaft 146 through the second horizontal hole. To be supplied to the lubrication target site.

Further, a second lubricating oil supply path 148 is provided in a region constituted by the third unit 146c in the crankshaft 146.
The second lubricating oil supply path 148 is opposed to the lubrication target portion from the inner peripheral surface to the outer peripheral surface of the vertical hole 148a in the third unit 146c and the vertical hole 148a formed along the axis from the lower end to the vicinity of the upper end of the third unit 146c. And a horizontal hole (not shown) provided up to the area to be operated.

  As a result, the lubricating oil that has entered the vertical hole 148a from the lower end of the crankshaft 146 is raised along the inner peripheral surface of the vertical hole 148a by the centrifugal force generated when the crankshaft 146 is rotationally driven, and each horizontal hole 148b. Through the crankshaft 146 and supplied to the lubrication target site.

  In this rotary compressor 131, in the compression mechanism section 133, the rear stage compression mechanism section 113 b that is at a higher temperature is located at the lower end of the housing 2 and is kept away from the drive section 4. Can be prevented, reliable and long life.

  Further, in the rotary compressor 131, a high pressure region H in which the exhaust of the rear compression mechanism portion 113 b is temporarily stored, that is, a high pressure side region in which the internal pressure is highest in the housing 2 is provided at the lower end portion of the housing 2. Therefore, since the housing 2 only needs to have a strength sufficient to withstand the final discharge pressure, only the lower end portion and the cylinder partition wall 136 constituting the high pressure side region H, the manufacturing cost can be reduced.

  In the rotary compressor 131, the second region S2, the low pressure region L, and the high pressure region H are provided in the housing 2 in the order in which the gas flows. Thus, the external compressor of the rotary compressor 131 can be made smaller.

It is a longitudinal section showing the composition of the rotary compressor concerning a first embodiment of the present invention. It is AA arrow sectional drawing of FIG. It is a longitudinal cross-sectional view which shows the structure of the compression mechanism part of the rotary compressor concerning 1st embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the rotary compressor concerning 2nd embodiment of this invention. It is a BB arrow sectional view of Drawing 4. It is CC sectional view taken on the line of FIG. It is DD sectional view taken on the line of FIG. It is EE arrow sectional drawing of FIG. It is a longitudinal cross-sectional view which shows the other structural example of the rotary compressor concerning 2nd embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the rotary compressor concerning 3rd embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the rotary compressor concerning 4th embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the rotary compressor concerning 5th embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the crankshaft of the rotary compressor concerning 5th embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the compression mechanism part of the rotary compressor concerning 6th embodiment of this invention.

Explanation of symbols

1, 51, 71, 81, 101, 111, 131 Rotary compressor 2 Housing 3, 53, 83, 103, 113, 133 Compression mechanism part 4 Drive parts 11a to 11e First to fifth cylinders 12 Cylindrical inner surface 13, 63, 73 Separator 13a Opening portion 14 Rotors 16, 86, 126, 146 Crankshafts 16a-16d First to fourth units 17 Eccentric shaft portion 28 Blade 29 Intermediate portion bearing 37 Lubricating oil supply path 41 Connection portion 66 Discharge path 67, 77 Oil separator 93 Second separator 106 Main partition walls 116, 136 Cylinder partition walls 126a-126c First to third units 127, 147 First lubricating oil supply paths 128, 148 Second lubricating oil supply paths 146a-146c First-first Three units H High pressure region S1 First region S2 Second region SH High pressure space SL Low pressure space

Claims (9)

A compression mechanism section that compresses gas; and a drive section that drives the compression mechanism section. The compression mechanism section includes a cylindrical inner surface and a plurality of cylinders in which the rotor is housed are separators between each other. The blades are arranged adjacent to each other in the axial direction in a state of sandwiching the cylinder, and each of the cylinders is urged in a direction protruding from the cylindrical inner surface to partition the space in the cylinder into a low pressure space and a high pressure space together with the rotor. A crankshaft that is provided and engages with each of the rotors is inserted into each of the cylinders and the separator, and each of the rotors is moved in each cylinder by rotating the crankshaft by the drive unit. A rotary compressor that is eccentrically rotated to compress the atmosphere in each cylinder,
Each separator is provided with an opening through which the crankshaft is inserted,
The crankshaft is configured to connect a plurality of units each provided with one eccentric shaft portion that engages with the rotor,
At least one of the units to be connected is provided with a connecting portion having a smaller diameter than the eccentric shaft portion, and the units to be connected are inserted through the opening of the separator. The rotary compressor is connected by the connecting portion in a state.   The rotary compressor according to claim 1, wherein a bearing that supports the connecting portion is provided in the opening of the separator.   The rotary compressor according to claim 2, wherein the crankshaft is provided with a lubricating oil supply path for supplying lubricating oil to a sliding surface with the bearing. The cylinders are arranged in the vertical direction,
In the separator, a discharge path that guides the compressed gas discharged from the cylinder located below to the downstream side of the flow path of the compressed gas in the rotary compressor,
4. An oil separator for separating lubricating oil from the compressed gas fed into the discharge path from the lower cylinder and returning it to the lower cylinder is provided. The rotary compressor according to crab. The crankshaft is held at one end side by the drive unit, and the driving force of the drive unit is input from the one end side,
2. The unit constituting the other end side of the crankshaft among the units constituting the crankshaft is made of a material that is lighter than the unit constituting the one end side. The rotary compressor according to any one of 4.   6. The rotary compressor according to claim 1, wherein at least some of the cylinders are connected in series on the gas flow path of the compression mechanism section. .   The rotary compressor according to claim 6, wherein, among the cylinders connected in series, a cylinder on the upstream side of the flow path is disposed on one end side of the crankshaft with respect to a cylinder on the downstream side. . The compression mechanism portion has a cylindrical shape with both ends closed, and is installed in a housing in which compressed gas discharged from at least one of the cylinders is temporarily stored, and at least the flow path of the cylinders In the most downstream cylinder, the blade is biased by the internal pressure of the housing,
The most downstream cylinder is disposed at an axial end of the housing;
In the housing, there is provided a cylinder partition that partitions a high-pressure area in which the most downstream cylinder is accommodated and an area in which the other cylinder is accommodated,
The rotary compressor according to claim 6 or 7, wherein compressed gas discharged from a cylinder used for compression at the last stage is supplied to the high pressure region. The compression mechanism part and the drive part are installed in the same housing,
In the housing, a main partition wall that partitions the space in the housing into a first region in which the compression mechanism portion is disposed and a second region in which the drive unit is disposed is provided,
The first region is a space for temporarily storing compressed gas discharged from at least one of the cylinders of the compression mechanism section,
The said 2nd area | region is made into the channel | path which passes before the gas of the compression object supplied to this rotary compressor is sent into the said compression mechanism part, The one in any one of Claim 1 to 8 characterized by the above-mentioned. Rotary compressor.

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