JP6785991B2 - Compressor - Google Patents

Description

The present invention relates to a compressor in which a plurality of compressor units are connected in parallel.

As this type of compressor, conventional compression has made it possible to obtain a wide capacity control range by connecting multiple compressor units with pressure equalizing pipes and oil equalizing pipes and changing the number of compressor units to be operated. There is a machine (see, for example, Patent Document 1). In Patent Document 1, each compressor unit includes a compression mechanism unit that compresses and discharges a refrigerant, and an electric motor unit that is arranged below the compression mechanism unit and drives the compression mechanism unit, and these are housed in a closed container. It has the above-mentioned configuration. The refrigerant compressed by the compression mechanism in each compressor unit is discharged into the upper space in the closed container, and the pressure equalizing pipe communicates with each other in the upper space of each compressor unit. Further, the oil leveling pipe communicates the oil reservoirs of the compressor units with each other.

In the compressor configured in this way, when one compressor unit is operating and the other compressor unit is stopped, the refrigerant discharged from the compression mechanism portion of the operating compressor unit is stopped. It flows into the compressor unit through a pressure equalizing pipe. As a result, the pressure inside the closed container of the stopped compressor unit is equalized by creating a high-pressure atmosphere similar to that of the operating compressor unit. By equalizing the pressure in this way, the refrigerating machine oil of the operating compressor unit flows out to the stopped compressor unit, causing a refueling failure in the operating compressor unit. I try to avoid.

Japanese Unexamined Patent Publication No. 7-35045

In Patent Document 1, the pressures of the operating compressor unit and the stopped compressor unit are equalized by communicating the upper spaces of the compressor units with each other by a pressure equalizing pipe. However, even if the pressure equalizing pipe is used, a pressure loss occurs until the refrigerant discharged from the operating compressor unit reaches the space in contact with the oil reservoir of the stopped compressor unit. The pressure drops. Therefore, when the pressure in the space in contact with the oil sump is compared between the compressor units, the stopped compressor unit is lower than the operating compressor unit. As a result, the refrigerating machine oil of the operating compressor unit may flow out to the stopped compressor through the oil leveling pipe, and the amount of refrigerating machine oil required for lubrication in the operating compressor unit may be insufficient. It was.

The present invention has been made in view of these points, and it is possible to prevent a shortage of refrigerating machine oil in the compressor unit during operation in a compressor in which a plurality of compressor units are connected by a pressure equalizing pipe and an oil equalizing pipe. The purpose is to provide a compressor.

The compressor according to the present invention is a compressor in which a plurality of compressor units are connected by a pressure equalizing pipe and an oil equalizing pipe, and each of the plurality of compressor units has a compression mechanism unit that compresses and discharges a refrigerant. An electric motor unit located below the compressor unit to drive the compressor unit, a closed container for accommodating the compressor unit and the electric motor unit, and an oil reservoir provided at the bottom of the airtight container for storing refrigerating machine oil. The plurality of compressor units include a first compressor unit that operates regardless of the load and a second compressor unit that operates when a preset load is exceeded, and the pressure equalizing pipe is the first. The upper space above the compression mechanism in the closed container of the compressor unit and the lower space below the compression mechanism in the closed container of the second compressor unit are communicated with each other, and the oil leveling pipe is a plurality of compressor units. oil reservoir portion communicated with the first compressor unit is provided with a guide for guiding the refrigerant discharged from the discharge port of the compression mechanism portion to pressure equalizing pipe, the guide opening of the one end faces the discharge port, the other The opening on the end side is provided with a flow path hole facing the opening of the pressure equalizing pipe .

According to the present invention, the upper space of the first compressor unit and the lower space of the second compressor unit are communicated with each other by a pressure equalizing pipe, so that the first compressor unit operates and the second compressor unit operates. Comparing the pressures of the second lower spaces in contact with the oil sump when stopped, the stopped second compressor unit is higher than the operating first compressor unit. Due to this pressure difference, the refrigerating machine oil moves from the stopped second compressor unit to the operating first compressor unit, so that it is possible to prevent a shortage of refrigerating machine oil in the operating first compressor unit.

It is a schematic vertical sectional view of the compressor which concerns on Embodiment 1 of this invention. It is a schematic vertical sectional view of each compressor unit constituting the compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of the operation range of each compressor unit which comprises the compressor which concerns on Embodiment 1 of this invention. It is a schematic vertical sectional view of the compressor which concerns on Embodiment 2 of this invention. It is an enlarged schematic sectional view of the main part of the 1st compressor unit of the compressor which concerns on Embodiment 3 of this invention. It is a schematic vertical sectional view of the compressor which concerns on Embodiment 4 of this invention. It is a schematic vertical sectional view of the compressor which concerns on Embodiment 5 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments described below. Hereinafter, as a compressor in which a plurality of compressor units are connected in parallel, a closed type compressor in which two compressor units are connected in parallel will be described.

Embodiment 1.
FIG. 1 is a schematic vertical sectional view of the compressor according to the first embodiment of the present invention.
The compressor includes a compressor unit 100a and a compressor unit 100b, and the compressor unit 100a and the compressor unit 100b are connected by a pressure equalizing pipe 70 and an oil equalizing pipe 71. The compressor unit 100a and the compressor unit 100b have the same configuration except that the connection positions of the pressure equalizing pipe 70 and the oil equalizing pipe 71 are different, and the configuration will be described with reference to FIG.

FIG. 2 is a schematic vertical sectional view of a compressor unit of the compressor according to the first embodiment of the present invention. In FIG. 1 above, the same components of the compressor unit 100a and the compressor unit 100b are provided with a subscript a on the compressor unit 100a side and a subscript b on the compressor unit 100b side. In FIG. 2, the subscript is omitted. In the following, when the compressor unit 100a and the compressor unit 100b are not distinguished, the subscripts shall be omitted. Further, in FIG. 2, the pressure equalizing pipe 70 is not shown.

The compressor unit 100 houses a compression mechanism unit 10 and an electric motor unit 20 that drives the compression mechanism unit 10 inside the closed container 1, and both are connected by a first shaft 30. The first shaft 30 transmits the rotational force of the electric motor unit 20 to the compression mechanism unit 10. The bottom of the closed container 1 is an oil reservoir 60 for storing refrigerating machine oil. The refrigerating machine oil stored in the oil reservoir 60 is sucked up by the oil supply mechanism 61 provided at the lower end of the first shaft 30 and supplied to each sliding portion.

The closed container 1 is provided with a suction pipe 51 that sucks an external refrigerant into the closed container 1 so as to penetrate the closed container 1, and the end portion of the suction pipe 51 in the closed container 1 is a fixed scroll 11 described later of the compression mechanism unit 10. Is press-fitted into. Further, a discharge pipe 52 for discharging the compressed refrigerant to the outside of the closed container 1 is connected to the closed container 1.

The compression mechanism portion 10 includes a fixed scroll 11 and a swing scroll 12, and spiral teeth and spiral teeth are provided on facing surfaces thereof, respectively. The spiral teeth and the spiral teeth are slidably meshed with each other to form a compression chamber 15 for compressing the refrigerant.

A discharge port 13 for discharging the compressed refrigerant is formed in the central portion of the fixed scroll 11. The discharge port 13 is open to the upper space 16 described later, and the refrigerant discharged from the discharge port 13 flows into the upper space 16. The fixed scroll 11 is fastened to the guide frame 2 fixedly supported in the closed container 1 by bolts or the like.

The swing scroll 12 includes a swing bearing 14, and rotatably supports the swing shaft portion 31 at the upper end of the first shaft 30. Further, the old dam mechanism 40 is engaged with the swing scroll 12 so as to be slidable back and forth. The oscillating scroll 12 is capable of eccentric turning motion without rotating with respect to the fixed scroll 11 by the Oldham mechanism 40.

The electric motor unit 20 has a rotor 21 and a stator 22, and is arranged below the compression mechanism unit 10. The rotor 21 is fixed to the first shaft 30 by shrink fitting or the like. The rotor 21 is rotationally driven by energizing the stator 22 to rotate the first shaft 30. Then, the compression mechanism unit 10 is driven by the rotation of the first shaft 30.

The inside of the closed container 1 has an upper space 16 above the compression mechanism portion 10 and a lower space 17 below the compression mechanism portion 10. The lower space 17 has a first lower space 18 above the electric motor portion 20, and a second lower space 19 below the electric motor portion 20 and in contact with the oil sump portion 60. A discharge pipe 52 connected through the closed container 1 communicates with the first lower space 18, and the refrigerant in the first lower space 18 is discharged to the refrigeration cycle (not shown) by the discharge pipe 52. It is supposed to be done.

In the closed container 1, the upper space 16 and the lower space 17 from which the refrigerant compressed by the compression mechanism portion 10 is discharged are the gap between the closed container 1 and the compression mechanism portion 10 and the gap between the components of the electric motor portion 20. It communicates through such as. Therefore, the closed container 1 is a so-called high-pressure container type in which the inside of the closed container 1 is filled with the refrigerant of the discharge pressure discharged from the compression mechanism unit 10.

FIG. 3 is an explanatory diagram of an operating range of each compressor unit constituting the compressor according to the first embodiment of the present invention. In FIG. 3, the horizontal axis represents the load [W / m ² ] and the vertical axis represents the capacity [kW].
The area indicated by dots in FIG. 3 indicates the operating range of the compressor unit 100a, and the area indicated by hatching indicates the operating range of the compressor unit 100b. The compressor unit 100a is a compressor that produces a maximum capacity of Y3-Y2, and the compressor unit 100b is a compressor that produces a maximum capacity of Y2. More specifically, the compressor unit 100a is a variable speed compressor capable of varying the operating frequency by driving an inverter, and the compressor unit 100b is a constant speed compressor having a constant operating frequency. Then, in this compressor, at a load of 0 to X or less, only the compressor unit 100a operates while changing the capacity according to the load to produce the capacity up to Y1. With a load exceeding X, both the compressor unit 100a and the compressor unit 100b operate, so that the capacity up to Y3 can be obtained.

In this way, the compressor can have a wide capacity control range by changing the number of operating compressor units. Here, the compressor unit 100a is a variable speed compressor, and the compressor unit 100b is a constant speed compressor, but the present invention is not limited to this. For example, both the compressor unit 100a and the compressor unit 100b may be configured by a variable speed compressor.

Since the compressor unit 100a is always operated regardless of the load, the compressor unit 100a will be referred to as the first compressor unit 100a below. Further, since the compressor unit 100b does not operate under a preset load X or less, but operates only at a high load exceeding the load X, the compressor unit 100b is referred to as the second compressor unit 100b below. That is. Here, the first compressor unit 100a corresponds to the first compressor unit of the present invention, and the second compressor unit 100b corresponds to the second compressor unit of the present invention.

Here, the description returns to FIG.
The compressor includes a pressure equalizing pipe 70 that communicates the upper space 16a of the first compressor unit 100a and the first lower space 18b of the second compressor unit 100b. The inner diameter of the pressure equalizing pipe 70 is larger than the equivalent hydraulic diameter of the cross-sectional area perpendicular to the first axis 30 in the gap between the closed container 1a and the compression mechanism portion 10a in order to reduce the pressure loss when passing through the pressure equalizing pipe 70. It is also desirable to increase.

Further, the compressor is provided with an oil leveling pipe 71 that connects the oil sump portion 60a of the first compressor unit 100a and the oil sump portion 60b of the second compressor unit 100b. It is desirable that the oil leveling pipe 71 be installed above the height of the suction port 62 at the lower end of the oil supply mechanism 61. The reason will be described later.

The operation of the compressor configured as described above will be described for each operating condition of each compressor unit.

<When the first compressor unit 100a is operating and the second compressor unit 100b is stopped>
The first compressor unit 100a takes in the low-temperature low-pressure refrigerant from the suction pipe 51a into the compression chamber 15a of the compression mechanism unit 10a, and the oscillating scroll 12a rotates eccentrically with the rotation of the first shaft 30a to take in the refrigerant. Compress. At this time, the refrigerating machine oil sucked up from the oil sump portion 60a at the bottom of the compressor is guided to the compression mechanism portion 10a.

The refrigerant compressed by the compression mechanism unit 10a is discharged from the discharge port 13a into the upper space 16a. The refrigerant discharged into the upper space 16a spreads in the upper space 16a from the center of the compressor toward the side surface of the closed container 1a, passes through the gap between the closed container 1a and the compression mechanism portion 10a, and reaches the first lower space 18a. To reach. Then, the refrigerant that has reached the first lower space 18a passes through the gap between the electric motor portion 20a and the closed container 1a, and reaches the second lower space 19a. The refrigerant that has reached the second lower space 19a passes through the air hole (not shown) of the rotor 21a and returns to the first lower space 18a again. Then, the refrigerant in the first lower space 18a is discharged from the discharge pipe 52a and circulates in the refrigeration cycle (not shown).

Further, a part of the refrigerant discharged from the discharge port 13a into the upper space 16a and spread from the center of the compressor toward the side surface of the closed container 1a flows into the pressure equalizing pipe 70, and the second compressor unit 100b is stopped. 1 Guided to the lower space 18b.

The refrigerant guided to the first lower space 18b of the compression mechanism unit 10b is a refrigerant discharged directly from the discharge port 13a of the first compressor unit 100a. That is, the refrigerant guided to the first lower space 18b of the compression mechanism portion 10b has a gap between the closed container 1a and the compression mechanism portion 10a like the refrigerant in the first lower space 18a of the first compressor unit 100a. It is not the refrigerant that has passed. Therefore, the pressure loss of the refrigerant guided to the first lower space 18b of the second compressor unit 100b that is stopped is the pressure loss of the refrigerant in the first lower space 18a of the operating first compressor unit 100a. Smaller than Therefore, the pressure in the first lower space 18b of the second compressor unit 100b that is stopped is higher than the pressure in the first lower space 18a of the operating first compressor unit 100a. Therefore, the pressure of the second lower space 19b communicating with the first lower space 18b is also higher than that of the second lower space 19a of the operating first compressor unit 100a.

As described above, there is a pressure difference between the second lower space 19a and the second lower space 19b, and due to this pressure difference, the first compressor unit operating from the stopped second compressor unit 100b The refrigerating machine oil moves to 100a via the oil leveling pipe 71. As a result, the amount of refrigerating machine oil required for lubrication can be secured in the operating first compressor unit 100a. Then, when the refrigerating machine oil moves through the oil leveling pipe 71 in this way, the oil level height of the second compressor unit 100b that is stopped naturally becomes equal to or higher than the installation height of the oil leveling pipe 71. ing. Therefore, if the installation height of the oil leveling pipe 71 is set higher than the suction port 62b of the oil supply mechanism 61b, the suction port 62b of the oil supply mechanism 61b can always be immersed in the refrigerating machine oil. As a result, even when the second compressor unit 100b starts to start with a load exceeding X, there is no risk that the second compressor unit 100b will run out of refrigerating machine oil.

<When both the first compressor unit 100a and the second compressor unit 100b are operating>
The first compressor unit 100a and the second compressor unit 100b take in the low-temperature low-pressure refrigerant from the suction pipe 51 into the compression chamber 15, compress the refrigerant, and discharge the refrigerant from the discharge port 13 into the upper space 16.

The refrigerant discharged from the compression mechanism portion 10b of the second compressor unit 100b is discharged into the upper space 16b and then flows into the first lower space 18b. On the other hand, the refrigerant discharged from the compression mechanism portion 10a of the first compressor unit 100a is discharged into the upper space 16a and then flows into the first lower space 18b of the second compressor unit 100b via the pressure equalizing pipe 70. .. The flow of the refrigerant flowing from the pressure equalizing pipe 70 into the first lower space 18b is obstructed by the refrigerant flowing from the upper space 16b to the lower space 17b in the second compressor unit 100b, and the flow of the refrigerant in the pressure equalizing pipe 70 is reduced. ..

Therefore, the pressure in the second lower space 19 in contact with the oil reservoirs 60 of the first compressor unit 100a and the second compressor unit 100b is uniformly increased by the refrigerant discharged from the respective compression mechanism units 10. Become. Therefore, the oil level height of each oil sump portion 60 is made uniform. As a result, the refrigerating machine oil is stably guided to each of the compression mechanism portion 10a and the compression mechanism portion 10b, and a good lubrication state can be obtained.

As described above, according to the first embodiment, the upper space 16a of the first compressor unit 100a and the first lower space 18b of the second compressor unit 100b are communicated with each other by the pressure equalizing pipe 70, and thus the following effects are obtained. Is obtained. That is, when the first compressor unit 100a is in operation and the second compressor unit 100b is stopped, the refrigerant discharged into the upper space 16a of the first compressor unit 100a is not increased in pressure loss. It can be led to the lower space 17b of the second compressor unit 100b. Therefore, when comparing the pressures of the second lower space 19 in contact with the oil reservoir 60 between the compressor units 100, the stopped second compressor unit 100b is operating the first compressor unit 100a. Will be higher than. Therefore, the refrigerating machine oil moves from the stopped second compressor unit 100b to the operating first compressor unit 100a, and the refrigerating machine oil amount required for lubrication can be secured in the first compressor unit 100a and refrigerated. It is possible to prevent a shortage of machine oil.

Further, the inner diameter of the pressure equalizing pipe 70 is larger than the equivalent hydraulic diameter of the cross-sectional area perpendicular to the first axis 30 in the gap between the closed container 1a and the compression mechanism portion 10a. Therefore, the pressure loss when the refrigerant passes through the pressure equalizing pipe 70 can be made smaller than the pressure loss when the refrigerant passes through the gap between the closed container 1a and the compression mechanism portion 10a. As a result, the pressure in the second lower space 19b of the compression mechanism portion 10b can be effectively increased more than the pressure in the second lower space 19b of the compression mechanism portion 10a.

In the first embodiment, the pressure equalizing pipe 70 is used to communicate the upper space 16a of the first compressor unit 100a with the lower space 17b of the second compressor unit 100b, so that the second compressor unit 100b to the first The refrigerating machine oil can be sufficiently transferred to the compressor unit 100a. On the other hand, a configuration is also conceivable in which the tip of the pressure equalizing pipe 70 on the second compressor unit 100b side is branched in two directions, one is connected to the lower space 17a, and the other is connected to the lower space 17b. That is, a configuration is also conceivable in which the upper space 16a of the first compressor unit 100a communicates with both the lower space 17a and the lower space 17b.

In such a configuration, when both the first compressor unit 100a and the second compressor unit 100b are operating, the same effect as that of the present invention can be obtained. However, when the second compressor unit 100b is stopped, the refrigerant that has flowed into the pressure equalizing pipe 70 from the upper space 16a of the first compressor unit 100a is divided into a lower space 17a and a lower space 17b. Therefore, the flow rate of the refrigerant from the first compressor unit 100a to the second compressor unit 100b is reduced as compared with the configuration in which the refrigerant flows only into the lower space 17b. Therefore, the pressure in the lower space 17b of the second compressor unit 100b is less likely to increase, and the movement of the refrigerating machine oil from the second compressor unit 100b to the first compressor unit 100a may be insufficient. Therefore, it is desirable that the tip of the pressure equalizing pipe 70 is connected only to the lower space 17b without branching the tip of the pressure equalizing pipe 70.

Embodiment 2.
In the second embodiment, the connection position of the pressure equalizing pipe 70 to the second compressor unit 100b is different from that of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described, and the configurations not described in the second embodiment are the same as those in the first embodiment.

FIG. 4 is a schematic vertical sectional view of the compressor according to the second embodiment of the present invention.
The compressor of the second embodiment is the same as the first embodiment in that one end of the pressure equalizing pipe 70 communicates with the upper space 16a of the first compressor unit 100a, but the other end of the pressure equalizing pipe 70 is second-compressed. It is different from the first embodiment in that it communicates with the second lower space 19b of the machine unit 100b.

With this configuration, when the first compressor unit 100a is operating and the second compressor unit 100b is stopped, the refrigerant discharged into the upper space 16a of the first compressor unit 100a is a pressure equalizing pipe. It is guided to the second lower space 19b of the second compressor unit 100b that has passed through 70 and is stopped, that is, the second lower space 19b that is in contact with the oil sump portion 60b.

The refrigerant guided to the second lower space 19b directly passes through the gap between the compression mechanism portion 10b of the second compressor unit 100b and the closed container 1b and the gap of the electric motor portion 20b, which is stopped, and directly in the upper space 16a. It is a refrigerant derived from, and has a small pressure loss. Therefore, the configuration of the second embodiment can increase the pressure of the second lower space 19b as compared with the configuration of the first embodiment. Therefore, the refrigerating machine oil can be effectively moved to the operating first compressor unit 100a, and the amount of refrigerating machine oil stored required for lubrication of the operating first compressor unit 100a can be stabilized. Can be secured.

When both the first compressor unit 100a and the second compressor unit 100b are in operation, the flow of the refrigerant flowing from the pressure equalizing pipe 70 into the second lower space 19b is the same as in the first embodiment. Decreases. Therefore, the pressure in the second lower space 19 in contact with the oil sump 60 of each of the first compressor unit 100a and the second compressor unit 100b is increased by the refrigerant discharged from each compression mechanism 10 to be uniform. become. Therefore, the oil level height of each oil sump portion 60 is made uniform. As a result, the refrigerating machine oil is stably guided to each of the compression mechanism portion 10a and the compression mechanism portion 10b, and a good lubrication state can be obtained.

As described above, according to the second embodiment, the same effect as that of the first embodiment can be obtained, and the connection position of the pressure equalizing pipe 70 to the second compressor unit 100b is set to the position communicating with the second lower space 19b. Therefore, the following effects can be obtained. That is, the pressure in the second lower space 19b when the first compressor unit 100a is operating and the second compressor unit 100b is stopped can be increased as compared with the first embodiment. As a result, in the second embodiment, the amount of refrigerating machine oil stored in the first compressor unit 100a in operation can be secured more stably than in the first embodiment.

Embodiment 3.
In the third embodiment, the configuration of the first compressor unit 100a is different from that of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described, and the configurations not described in the third embodiment are the same as those in the first embodiment.

FIG. 5 is an enlarged schematic cross-sectional view of a main part of the first compressor unit of the compressor according to the third embodiment of the present invention.
The compressor of the third embodiment has a configuration in which the first compressor unit 100a of the compressor of the first embodiment is further provided with a guide 80 for guiding the refrigerant discharged from the discharge port 13a to the pressure equalizing pipe 70. The guide 80 is installed on the upper surface of the fixed scroll 11a, and has a hollow shape having an opening 81a on one end facing the discharge port 13a and an opening 81b on the other end facing the opening of the pressure equalizing pipe 70. It is configured in.

According to the third embodiment, the same effect as that of the first embodiment can be obtained, and the following effects can be further obtained by providing the guide 80. That is, the refrigerant discharged from the discharge port 13a is easily guided by the guide 80 and flows into the pressure equalizing pipe 70, and the pressure loss of the refrigerant when flowing into the pressure equalizing pipe 70 can be reduced. Therefore, the pressure in the second lower space 19b of the stopped second compressor unit 100b can be made higher than the pressure in the second lower space 19b of the operating first compressor unit 100a. Therefore, the refrigerating machine oil can be moved more stably from the stopped second compressor unit 100b to the operating first compressor unit 100a via the oil leveling pipe 71. As a result, in the third embodiment, the amount of refrigerating machine oil stored in the first compressor unit 100a in operation can be secured more stably than in the first embodiment.

Embodiment 4.
In the fourth embodiment, the connection position of the pressure equalizing pipe 70 to the first compressor unit 100a is different from that of the first embodiment. Hereinafter, the differences from the first embodiment will be mainly described, and the configurations not described in the fourth embodiment are the same as those in the first embodiment.

FIG. 6 is a schematic vertical sectional view of the compressor according to the fourth embodiment of the present invention.
In the compressor of the fourth embodiment, the connection position of the pressure equalizing pipe 70 to the first compressor unit 100a is a position communicating with the upper space 16a in the first embodiment, which is the side surface of the closed container 1a. On the other hand, it differs from the first embodiment in that the upper surface of the closed container 1a is used. Further, the connection position of the pressure equalizing pipe 70 to the upper surface of the closed container 1a is directly above the discharge port 13a of the compression mechanism portion 10a. Further, the center of the opening 70a of the pressure equalizing pipe 70 is located on the central axis of the discharge port 13a.

Since the refrigerant discharged from the discharge port 13a has a flow velocity direction in the central axis direction of the discharge port 13a, it flows directly into the opening 70a of the pressure equalizing pipe 70 located on the central axis. Therefore, the pressure loss when the refrigerant discharged from the discharge port 13a flows into the pressure equalizing pipe 70 can be reduced. Therefore, the pressure in the second lower space 19b of the second compressor unit 100b that is stopped can be made higher than the pressure in the second lower space 19a of the operating first compressor unit 100a. As a result, the refrigerating machine oil can be moved from the stopped second compressor unit 100b to the operating first compressor unit 100a, which is necessary for lubricating the operating first compressor unit 100a. The amount of refrigerating machine oil stored can be secured.

As described above, according to the fourth embodiment, the same effect as that of the first embodiment can be obtained, and the connection position of the pressure equalizing pipe 70 to the first compressor unit 100a is compressed on the upper surface of the closed container 1a. Further, the following effects can be obtained by setting the mechanism portion 10a directly above the discharge port 13a. That is, the pressure loss when the refrigerant discharged from the discharge port 13a flows into the pressure equalizing pipe 70 can be reduced as compared with the first embodiment. Therefore, the pressure in the second lower space 19b of the stopped second compressor unit 100b can be made higher than the pressure in the second lower space 19b of the operating first compressor unit 100a. Therefore, the refrigerating machine oil can be moved more stably from the stopped second compressor unit 100b to the operating first compressor unit 100a via the oil leveling pipe 71. As a result, in the third embodiment, the amount of refrigerating machine oil stored in the first compressor unit 100a in operation can be secured more stably than in the first embodiment.

Embodiment 5.
The fifth embodiment relates to a technique for improving so-called refrigerant stagnation in which the refrigerant dissolves in the refrigerating machine oil. Hereinafter, the differences from the first embodiment will be mainly described, and the configurations not described in the fifth embodiment are the same as those in the first embodiment.

FIG. 7 is a schematic vertical sectional view of the compressor according to the fifth embodiment of the present invention.
The compressor of the fifth embodiment is further connected to the compressor of the first embodiment, one end is connected to the suction port 62a of the refueling mechanism 61a of the first compressor unit 100a, and the other end is the oil of the second compressor unit 100b. It has a configuration including a pipe 63 located in the pool portion 60b. The pipe 63 is arranged through the inside of the oil leveling pipe 71.

When the first compressor unit 100a is operating and the second compressor unit 100b is stopped, the refrigerant in the upper space 16a of the first compressor unit 100a is second-compressed via the pressure equalizing pipe 70 as described above. It flows into the lower space 17b of the machine unit 100b. Therefore, although the pressure of the refrigerant in the lower space 17b increases, the temperature inside the closed container 1b does not easily rise because the second compressor unit 100b is stopped, and the refrigerant easily dissolves in the refrigerating machine oil. Therefore, if no measures are taken, the first compressor unit 100a is operating and the second compressor unit 100b is stopped. Under the operating conditions, the refrigerant is always laid down on the second compressor unit 100b side. There is a possibility of becoming. Since the viscosity of the refrigerating machine oil decreases in the state where the refrigerant is laid down, the oil film may break at the sliding portion of the second compressor unit 100b at the start of the operation of the second compressor unit 100b, and seizure may occur.

Therefore, in the fifth embodiment, the pipe 63 is provided. By providing the pipe 63, the refrigerating machine oil in the oil reservoir 60b of the second compressor unit 100b is sucked up by the refueling mechanism 61a through the pipe 63 during the operation of the first compressor unit 100a. The sucked-up refrigerating machine oil lubricates the sliding portion in the first compressor unit 100a and then returns to the oil sump portion 60a. The refrigerating machine oil is warmed in the process of lubricating the sliding portion and returning to the oil sump portion 60a.

Then, the amount of oil in the oil sump 60b of the second compressor unit 100b is reduced from the amount of oil in the oil sump 60a of the first compressor unit 100a by sucking up by the oil supply mechanism 61a of the first compressor unit 100a. Therefore, the warmed refrigerating machine oil in the oil sump portion 60a moves through the oil leveling pipe 71 to the oil sump portion 60b of the second compressor unit 100b due to the height difference of the oil amount. As a result, the temperature of the refrigerating machine oil in the oil sump portion 60b rises, the refrigerant becomes difficult to dissolve in the refrigerating machine oil, and the oil viscosity of the refrigerating machine oil can be prevented from decreasing.

As described above, according to the fifth embodiment, the same effect as that of the first embodiment can be obtained, and the refrigerating machine oil is circulated and warmed between the compressor units by providing the pipe 63, and the oil viscosity of the refrigerating machine oil is increased. The decrease can be prevented.

Although the above embodiments have been described as separate embodiments in the first to fifth embodiments, the compressor may be configured by appropriately combining the characteristic configurations of the respective embodiments. For example, the second embodiment and the third embodiment may be combined, and the compressor of the second embodiment shown in FIG. 4 may be provided with the guide 80 of the third embodiment. Further, the second embodiment and the fourth embodiment may be combined. That is, in the compressor of the second embodiment shown in FIG. 4, the connection position of the pressure equalizing pipe 70 to the first compressor unit 100a is the upper surface of the closed container 1 as in the fourth embodiment, and the discharge port. It may be configured on the central axis of 13a. Further, the compressor of the third embodiment shown in FIG. 5 may be provided with the pipe 63 of the fifth embodiment.

1 closed container, 1a closed container, 1b closed container, 2 guide frame, 10 compression mechanism, 10a compression mechanism, 10b compression mechanism, 11 fixed scroll, 11a fixed scroll, 12 swing scroll, 12a swing scroll, 13 Discharge port, 13a Discharge port, 14 swing bearing, 15 compression chamber, 15a compression chamber, 16 upper space, 16a upper space, 16b upper space, 17 lower space, 17a lower space, 17b lower space, 18 first lower space, 18a 1st lower space, 18b 1st lower space, 19 2nd lower space, 19a 2nd lower space, 19b 2nd lower space, 20 electric motor part, 20a electric motor part, 20b electric motor part, 21 rotor, 21a rotor, 22 Rotor, 30 1st shaft, 30a 1st shaft, 31 Swing shaft, 40 Oldam mechanism, 51 Suction pipe, 51a Suction pipe, 52 Discharge pipe, 52a Discharge pipe, 60 Oil sump, 60a Oil sump, 60b oil sump, 61 oil supply mechanism, 61a oil supply mechanism, 61b oil supply mechanism, 62 suction port, 62a suction port, 62b suction port, 63 piping, 70 pressure equalizing pipe, 70a opening, 71 oil equalizing pipe, 80 guide, 80a flow path hole , 81a opening, 81b opening, 100 compressor unit, 100a compressor unit, 100b compressor unit.

Claims (7)

A compressor in which a plurality of compressor units are connected by a pressure equalizing pipe and an oil equalizing pipe.
Each of the plurality of compressor units
A compression mechanism that compresses and discharges the refrigerant,
An electric motor unit that is arranged below the compression mechanism unit and drives the compression mechanism unit,
A closed container that houses the compression mechanism and the electric motor,
It is provided at the bottom of the closed container and is provided with an oil reservoir for storing refrigerating machine oil.
The plurality of compressor units include a first compressor unit that operates regardless of a load, and a second compressor unit that operates when a preset load is exceeded.
The pressure equalizing pipe includes an upper space above the compression mechanism in the closed container of the first compressor unit and a lower space below the compression mechanism in the closed container of the second compressor unit. Communicate,
The oil equalizing tube, and communicating the oil reservoir portion of the plurality of compressor unit,
The first compressor unit includes a guide for guiding the refrigerant discharged from the discharge port of the compression mechanism unit to the pressure equalizing pipe, and the guide has an opening on one end facing the discharge port and on the other end. A compressor having a flow path hole whose opening faces the opening of the pressure equalizing pipe . It is a compressor in which a plurality of compressor units are connected by a pressure equalizing pipe and an oil equalizing pipe.
Each of the plurality of compressor units
A compression mechanism that compresses and discharges the refrigerant,
An electric motor unit that is arranged below the compression mechanism unit and drives the compression mechanism unit,
A closed container that houses the compression mechanism and the electric motor,
It is provided at the bottom of the closed container and is provided with an oil reservoir for storing refrigerating machine oil.
The plurality of compressor units include a first compressor unit that operates regardless of a load, and a second compressor unit that operates when a preset load is exceeded.
The pressure equalizing pipe includes an upper space above the compression mechanism portion in the closed container of the first compressor unit and a lower space below the compression mechanism portion in the closed container of the second compressor unit. Communicate,
The oil leveling pipe communicates with the oil sump portion of the plurality of compressor units.
Arranged through the inside of the oil leveling pipe, one end is connected to a suction port for refrigerating machine oil supplied to the sliding portion of the first compressor unit, and the other end is connected to the oil sump portion of the second compressor unit. Compressor with located piping. The lower space is divided into a first lower space between the compression mechanism portion and the electric motor portion and a second lower space below the electric motor portion, and one end of the pressure equalizing pipe is the first compressor. The compressor according to claim 1 or 2 , wherein the other end of the pressure equalizing pipe communicates with the upper space of the unit and communicates with the first lower space. The lower space is divided into a first lower space between the compression mechanism portion and the electric motor portion and a second lower space below the electric motor portion, and one end of the pressure equalizing pipe is the first compressor. The compressor according to claim 1 or 2, wherein the other end of the pressure equalizing pipe communicates with the upper space of the unit and communicates with the second lower space. The compression according to any one of claims 1 to 4 , wherein the opening of the pressure equalizing tube on the first compressor unit side is located directly above the discharge port of the compression mechanism portion of the first compressor unit. Machine. A first shaft that connects the electric motor unit and the compression mechanism unit and transmits the rotational force of the electric motor unit to the compression mechanism unit is provided.
Claims 1 to claim that the inner diameter of the pressure equalizing pipe is larger than the equivalent hydraulic diameter of the cross section of the first compressor unit between the closed container and the compression mechanism portion perpendicular to the first axis. 5. The compressor according to any one of 5 . The discharge port of the compression mechanism unit is open to the upper space, and the upper space and the lower space communicate with each other in the closed container, and the closed container discharges the discharge from the compression mechanism unit. The compressor according to any one of claims 1 to 6 , which is a high-pressure container type whose inside is filled with a pressure refrigerant.

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