JP5434746B2 - Turbo compressor and turbo refrigerator - Google Patents

Description

 The present invention relates to a turbo compressor and a turbo refrigerator.

 As a refrigerator that cools or freezes an object to be cooled such as water, a turbo refrigerator that includes a turbo compressor that compresses and discharges refrigerant by rotation of an impeller is known. A turbo compressor included in such a turbo refrigerator has a plurality of sliding portions such as bearings and gears that slide with the operation of a drive unit such as a motor. For this reason, the turbo compressor is provided with a lubricating oil supply structure for supplying lubricating oil for lubricating the sliding portion, for example, as shown in Patent Document 1. The lubricating oil supply structure includes an oil tank that stores the lubricating oil and a pump that feeds the lubricating oil toward the sliding portion.

JP 2009-257684 A

Incidentally, the lubricating oil supply structure may be provided with an adjustment valve that adjusts the flow rate of the lubricating oil supplied to the sliding portion. This adjustment valve is installed in the flow path which branches from the flow of the lubricating oil sent out from the pump, for example, and returns to the oil tank.
However, the pump and the regulating valve, and the regulating valve and the oil tank are connected by a plurality of pipes, resulting in an increase in the number of parts such as the pipes. As the number of parts such as pipes increases, the assembly work of the lubricating oil supply structure becomes complicated, and oil leakage is likely to occur from the connection points of the pipes.

 The present invention has been made in view of the above points, and is characterized by providing a turbo compressor and a turbo refrigerator that can reduce the number of parts such as piping connected to a regulating valve.

In order to solve the above problems, the present invention employs the following means.
A turbo compressor according to the present invention includes a pump that feeds lubricating oil stored in an oil tank having an opening, and a flow rate of lubricating oil that branches from the flow of lubricating oil sent from the pump and returns to the oil tank. A turbo compressor comprising an adjustment valve for adjustment, comprising an oil tank cover that seals an opening and is provided with an installation portion for the adjustment valve, the oil tank cover being opened to the installation portion and fed from a pump At least one of a first flow path in which the flow of the lubricating oil branches and flows toward the adjustment valve, and a second flow path that opens in the installation portion and flows from the adjustment valve toward the oil tank. Is adopted.
According to the present invention, since at least one of the first flow path and the second flow path is open in the installation portion, the adjustment valve is installed in the installation portion, whereby the first flow with respect to the adjustment valve. At least one of the path and the second flow path is directly connected.

The turbo compressor according to the present invention includes an oil filter that is installed in the oil tank cover and filters the lubricating oil sent out from the pump, and the first flow path is from a flow path between the pump and the oil filter. A configuration that is provided by branching is employed.
According to the present invention, the lubricating oil flowing through the regulating valve returns to the oil tank without passing through the oil filter. Therefore, the amount of lubricating oil filtered by the oil filter can be suppressed, and the filter life of the oil filter can be extended.

The turbo compressor according to the present invention employs a configuration in which the installation portion is formed in a flat shape.
According to the present invention, it is possible to easily ensure the liquid tightness between the oil tank cover installation portion and the regulating valve.

 The turbo refrigerator according to the present invention includes a condenser that cools and liquefies the compressed refrigerant, an evaporator that cools the object to be cooled by evaporating the liquefied refrigerant and taking heat of vaporization from the object to be cooled, A compressor that compresses the refrigerant evaporated in the evaporator and supplies the compressed refrigerant to the condenser, the compressor comprising the turbo compressor according to any one of claims 1 to 3; The configuration is adopted.

According to the present invention, the following effects can be obtained.
According to the present invention, by installing the adjustment valve in the installation portion, at least one of the first flow path and the second flow path is directly connected to the adjustment valve. Therefore, in the turbo compressor and the turbo refrigerator, there is an effect that the number of parts such as piping connected to the regulating valve can be reduced.

It is a block diagram which shows schematic structure of the turbo refrigerator in embodiment of this invention. It is a horizontal sectional view of a turbo compressor in an embodiment of the present invention. It is the schematic of the lubricating oil supply unit in embodiment of this invention.

 Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 3. In each drawing used for the following description, the scale of each member is appropriately changed to make each member a recognizable size.

FIG. 1 is a block diagram showing a schematic configuration of a turbo refrigerator S1 in the present embodiment.
The turbo chiller S1 in the present embodiment is installed in a building, a factory, or the like, for example, to generate cooling water for air conditioning. As shown in FIG. 1, the condenser 1, the economizer 2, and the evaporation And a turbo compressor 4.

 The condenser 1 is supplied with a compressed refrigerant gas X1, which is a compressed gaseous refrigerant, and cools and liquefies the compressed refrigerant gas X1 to obtain a refrigerant liquid X2. As shown in FIG. 1, the condenser 1 is connected to the turbo compressor 4 through a flow path R1 through which the compressed refrigerant gas X1 flows, and is connected to the economizer 2 through a flow path R2 through which the refrigerant liquid X2 flows. Has been. In addition, the expansion valve 5 for decompressing the refrigerant liquid X2 is installed in the flow path R2.

 The economizer 2 temporarily stores the refrigerant liquid X2 decompressed by the expansion valve 5. The economizer 2 is connected to the evaporator 3 via a flow path R3 through which the refrigerant liquid X2 flows. The economizer 2 is connected to the turbo compressor 4 through a flow path R4 through which the gas phase component X3 of the refrigerant generated in the economizer 2 flows. It is connected. Note that an expansion valve 6 for further reducing the pressure of the refrigerant liquid X2 is installed in the flow path R3. Further, the flow path R4 is connected to the turbo compressor 4 so as to supply a gas phase component X3 to a second compression stage 22 described later included in the turbo compressor 4.

 The evaporator 3 cools the object to be cooled by evaporating the refrigerant liquid X2 and removing the heat of vaporization from the object to be cooled such as water. The evaporator 3 is connected to the turbo compressor 4 via a flow path R5 through which a refrigerant gas X4 generated by evaporating the refrigerant liquid X2 flows. The flow path R5 is connected to a first compression stage 21 (described later) included in the turbo compressor 4.

 The turbo compressor 4 compresses the refrigerant gas X4 into a compressed refrigerant gas X1. The turbo compressor 4 is connected to the condenser 1 through the flow path R1 through which the compressed refrigerant gas X1 flows as described above, and is connected to the evaporator 3 through the flow path R5 through which the refrigerant gas X4 flows. Yes.

In the turbo chiller S1 configured as described above, the compressed refrigerant gas X1 supplied to the condenser 1 via the flow path R1 is liquefied and cooled by the condenser 1 to become a refrigerant liquid X2. The refrigerant liquid X2 is decompressed by the expansion valve 5 when supplied to the economizer 2 via the flow path R2, and is temporarily stored in the economizer 2 in a decompressed state, and then evaporated via the flow path R3. When supplied to the evaporator 3, the pressure is further reduced by the expansion valve 6, and the pressure is further reduced and supplied to the evaporator 3. The refrigerant liquid X2 supplied to the evaporator 3 is evaporated by the evaporator 3 to become the refrigerant gas X4, and is supplied to the turbo compressor 4 via the flow path R5. The refrigerant gas X4 supplied to the turbo compressor 4 is compressed by the turbo compressor 4 into the compressed refrigerant gas X1, and is supplied again to the condenser 1 via the flow path R1.
Note that the gas phase component X3 of the refrigerant generated when the refrigerant liquid X2 is stored in the economizer 2 is supplied to the turbo compressor 4 via the flow path R4, and is compressed together with the refrigerant gas X4 to be compressed refrigerant gas X1. Is supplied to the condenser 1 through the flow path R1.
And in such turbo refrigerator S1, when the refrigerant | coolant liquid X2 evaporates in the evaporator 3, it cools or refrigerates a cooling target object by taking heat of vaporization from a cooling target object.

Subsequently, the turbo compressor 4 including the characteristic part of the present embodiment will be described in more detail. FIG. 2 is a horizontal sectional view of the turbo compressor 4 in the present embodiment.
As shown in FIG. 2, the turbo compressor 4 in the present embodiment includes a motor unit 10, a compressor unit 20, and a gear unit 30.

The motor unit 10 includes an output shaft 11 and a motor 12 serving as a drive source for driving the compressor unit 20, and a motor casing 13 that surrounds the motor 12 and in which the motor 12 is installed. The drive source for driving the compressor unit 20 is not limited to the motor 12 and may be, for example, an internal combustion engine.
The output shaft 11 of the motor 12 is rotatably supported by a first bearing 14 and a second bearing 15 that are fixed to the motor casing 13.

 The compressor unit 20 sucks and compresses the refrigerant gas X4 (see FIG. 1), and further compresses the refrigerant gas X4 compressed in the first compression stage 21 to compress the compressed refrigerant gas X1 ( And a second compression stage 22 for discharging as shown in FIG.

The first compression stage 21 applies pressure energy to the refrigerant gas X4 supplied from the thrust direction and discharges it in the radial direction, and pressure energy applied to the refrigerant gas X4 by the first impeller 21a. A first diffuser 21b that compresses by converting it into energy, a first scroll chamber 21c that leads the refrigerant gas X4 compressed by the first diffuser 21b to the outside of the first compression stage 21, and a refrigerant gas X4 And a suction port 21d that supplies the first impeller 21a.
The first diffuser 21b, the first scroll chamber 21c, and the suction port 21d are formed by a first impeller casing 21e that surrounds the first impeller 21a.

In the compressor unit 20, a rotating shaft 23 extending between the first compression stage 21 and the second compression stage 22 is provided. The first impeller 21 a is fixed to the rotating shaft 23 and is driven to rotate when the rotational power of the motor 12 is transmitted to the rotating shaft 23.
A plurality of inlet guide vanes 21 f for adjusting the suction capacity of the first compression stage 21 are installed at the suction port 21 d of the first compression stage 21. Each inlet guide vane 21f is rotatable so that the apparent area from the flow direction of the refrigerant gas X4 can be changed by a drive mechanism 21g fixed to the first impeller casing 21e. Further, a vane drive unit 24 that is connected to the drive mechanism 21g and rotationally drives each inlet guide vane 21f is installed outside the first impeller casing 21e.

The second compression stage 22 is provided with a second impeller 22a which gives velocity energy to the refrigerant gas X4 supplied from the thrust direction after being compressed in the first compression stage 21 and discharges it in the radial direction, and a second impeller 22a. The second diffuser 22b that compresses the velocity energy imparted to the refrigerant gas X4 into pressure energy and discharges it as the compressed refrigerant gas X1, and the compressed refrigerant gas X1 discharged from the second diffuser 22b into the second compression stage. 22 is provided with a second scroll chamber 22c led out to the outside of 22 and an introduction scroll chamber 22d for guiding the refrigerant gas X4 compressed in the first compression stage 21 to the second impeller 22a.
The second diffuser 22b, the second scroll chamber 22c, and the introduction scroll chamber 22d are formed by a second impeller casing 22e that surrounds the second impeller 22a.

The second impeller 22a is fixed to the rotary shaft 23 so as to be back-to-back with the first impeller 21a, and is driven to rotate by transmitting the rotational power of the motor 12 to the rotary shaft 23.
The second scroll chamber 22c is connected to a flow path R1 (see FIG. 1) for supplying the compressed refrigerant gas X1 to the condenser 1 (see FIG. 1), and the compressed refrigerant gas derived from the second compression stage 22 is used. X1 is supplied to the flow path R1.

 The first scroll chamber 21c of the first compression stage 21 and the introduction scroll chamber 22d of the second compression stage 22 are external pipes provided separately from the first compression stage 21 and the second compression stage 22 (see FIG. The refrigerant gas X4 compressed in the first compression stage 21 is supplied to the second compression stage 22 through the external pipe. The above-described flow path R4 (see FIG. 1) is connected to the external pipe, and the refrigerant gas phase component X3 generated in the economizer 2 is supplied to the second compression stage 22 via the external pipe. It has become.

 The rotary shaft 23 includes a third bearing 26 fixed to the second impeller casing 22e in a space 25 between the first compression stage 21 and the second compression stage 22, and an end of the second impeller casing 22e on the gear unit 30 side. A fourth bearing 27 fixed to the part is rotatably supported.

The gear unit 30 is for transmitting the rotational power of the motor 12 to the rotary shaft 23, and is a flat gear 31 fixed to the output shaft 11 and a pinion fixed to the rotary shaft 23 and meshing with the flat gear 31. A gear 32 and a gear casing 33 that accommodates the spur gear 31 and the pinion gear 32 are provided.
Furthermore, the gear unit 30 is provided in the gear casing 33 and stores an oil tank 34 that stores the lubricating oil, and a nozzle 35 that injects and supplies the lubricating oil to a sliding portion that slides as the motor 12 operates. A supply pipe 36 connected to the nozzle 35, and a lubricant supply unit 40 (hereinafter simply referred to as “supply unit 40”) that sends the lubricant stored in the oil tank 34 toward the supply pipe 36 and the nozzle 35. I have. Examples of the sliding portion described above include a bearing such as the fourth bearing 27 or the meshing portion of the spur gear 31 and the pinion gear 32.

 The spur gear 31 has an outer diameter larger than that of the pinion gear 32, and the spur gear 31 and the pinion gear 32 cooperate to increase the rotational speed of the rotary shaft 23 relative to the rotational speed of the output shaft 11. The rotational power of the motor 12 is transmitted to the rotary shaft 23. In addition, it is not limited to such a transmission method, You may set the diameter of a some gearwheel so that the rotation speed of the rotating shaft 23 may be the same number or it may reduce with respect to the rotation speed of the output shaft 11. FIG.

 The gear casing 33 is formed separately from the motor casing 13 and the second impeller casing 22e, and connects the two. A housing space 33 a for housing the spur gear 31, the pinion gear 32, the nozzle 35, and the supply pipe 36 is formed inside the gear casing 33.

 The oil tank 34 is a tank for collecting and storing the lubricating oil that has been supplied and lubricated to the sliding portion that slides with the operation of the motor 12. The lubricating oil stored in the oil tank 34 may contain fine metal powder or sludge generated at the sliding portion.

 The nozzle 35 injects and supplies lubricating oil in order to lubricate the sliding parts such as the fourth bearing 27 and the meshing part of the spur gear 31 and the pinion gear 32. The supply pipe 36 is a pipe member that is provided between the nozzle 35 and the supply unit 40 and supplies lubricating oil to the nozzle 35. In addition, you may provide the other nozzle which supplies lubricating oil to sliding locations, such as the 1st bearing 14 and the 3rd bearing 26. FIG.

Next, the supply unit 40 that is a characteristic part of the present embodiment will be described in more detail. 3A and 3B are schematic views of the supply unit 40 in the present embodiment, where FIG. 3A is a front view, FIG. 3B is a plan view, and FIG. 3C is a side view.
The supply unit 40 includes a pump 41, an oil filter 42, a first closing valve 43, a second closing valve 44, and an adjustment valve 45. The pump 41, the oil filter 42, the first closing valve 43, the second closing valve 44 and the adjustment valve 45 are all installed in the oil tank cover 46. The oil tank cover 46 is provided by sealing an opening 34 a formed in the oil tank 34. The oil tank cover 46 is formed by using, for example, a casting method, and is fixed to the oil tank 34 by a plurality of fastening bolts 46a.
Note that a second supply pipe 47 is connected to the supply unit 40. The second supply pipe 47 is a pipe member connected to the supply pipe 36 (see FIG. 2).

The pump 41 is installed on the back side of the oil tank cover 46 and is provided inside the oil tank 34. The pump 41 sends the lubricating oil stored in the oil tank 34 toward the first pre-filtration flow path 46 b formed in the oil tank cover 46. The discharge amount from the pump 41 is constant.
The oil filter 42 is replaceably installed in a filter installation space 46 c formed on the front side of the oil tank cover 46. The oil filter 42 is for filtering the lubricating oil sent from the pump 41 and removing fine metal powder, sludge and the like contained in the lubricating oil.

 The first closing valve 43 is installed on the front side of the oil tank cover 46. The first closing valve 43 is connected to the pump 41 via the first pre-filtration flow path 46 b and is connected to the filter installation space 46 c via the second pre-filtration flow path 46 d formed in the oil tank cover 46. . The first closing valve 43 is a valve that closes the first pre-filtration flow path 46b and the second pre-filtration flow path 46d and blocks the flow of the lubricating oil toward the oil filter 42. The first closing valve 43 is opened and closed by operating the first knob 43a.

 The second closing valve 44 is installed between the filter installation space 46 c and the second supply pipe 47 on the front side of the oil tank cover 46. The second closing valve 44 is a valve that closes the space between the filter installation space 46 c and the second supply pipe 47 and blocks the flow of the lubricating oil toward the supply pipe 36. The second closing valve 44 is opened and closed by operating the second knob 44a.

 The adjustment valve 45 is a valve that adjusts the flow rate of the lubricating oil branched from the flow of the lubricating oil sent from the pump 41 and returning to the oil tank 34. The adjustment valve 45 is installed in an installation part 46 e formed in the oil tank cover 46. A surface of the regulating valve 45 facing the installation portion 46e is formed in a flat shape, and an inflow hole and an outflow hole (not shown) are provided on this surface. The flow rate of the lubricating oil entering the adjustment valve 45 from the inflow hole and flowing out from the outflow hole is adjustable. The flow rate of the lubricating oil is adjusted by operating the third knob 45a.

 The installation part 46e is formed in a planar shape. A gasket (seal member) (not shown) is held between the adjustment valve 45 and the installation portion 46e to keep the space between them. Note that through holes are formed in the gasket at positions corresponding to the inflow hole and the outflow hole of the adjustment valve 45, respectively. Since the surface of the regulating valve 45 facing the installation portion 46e and the installation portion 46e are both formed in a flat shape, liquid tightness between them can be easily ensured.

Further, the oil tank cover 46 is formed with a branch channel 46f (first channel) and a return channel 46g (second channel).
The branch flow path 46f branches off from the filter installation space 46c and opens to the installation part 46e. That is, the branch flow path 46f is branched from the flow path between the pump 41 and the oil filter 42. The opening position of the branch channel 46f at the installation portion 46e is a position facing the inflow hole of the adjustment valve 45. As described above, since the gasket is sandwiched between the adjustment valve 45 and the installation portion 46e, the branch flow path 46f is liquid-tightly connected to the inflow hole of the adjustment valve 45. That is, the branch flow path 46f directly connects the filter installation space 46c and the adjustment valve 45. The branch channel 46f has a plurality of extending hole portions that extend in a predetermined direction, and a predetermined end portion of the extending hole portion is provided with a set screw 46h (slotted set screw). Screwed and sealed.

 The return flow path 46g is provided between the installation portion 46e and the back side of the oil tank cover 46. One end of the return flow path 46g opens to the installation portion 46e, and the other end opens to the back side of the oil tank cover 46 (ie, inside the oil tank 34). The opening position of the return channel 46g at the installation portion 46e is a position facing the outflow hole of the adjustment valve 45. As described above, since the gasket is sandwiched between the adjustment valve 45 and the installation portion 46e, the return flow path 46g is liquid-tightly connected to the outflow hole of the adjustment valve 45. That is, the return flow path 46g directly connects the regulating valve 45 and the inside of the oil tank 34.

Here, the supply operation of the lubricating oil in the supply unit 40 will be described.
First, the first closing valve 43 and the second closing valve 44 are opened by operating the first knob 43a and the second knob 44a.
By the operation of the pump 41, the lubricating oil stored in the oil tank 34 is sent out toward the first pre-filtration channel 46b. The lubricating oil sent out to the first pre-filtration flow path 46b flows into the filter installation space 46c through the first closing valve 43 and the second pre-filtration flow path 46d. The lubricating oil flows into the oil filter 42 installed in the filter installation space 46c and is filtered. By this filtration, fine metal powder, sludge and the like contained in the lubricating oil are removed. The lubricating oil filtered by the oil filter 42 is sent out to the second supply pipe 47 through the second closing valve 44. The lubricating oil sent to the second supply pipe 47 is supplied to the nozzle 35 through the supply pipe 36 and is jetted from the nozzle 35 toward the sliding portion.

A part of the lubricating oil flowing into the filter installation space 46 c flows through the branch flow path 46 f and flows into the adjustment valve 45. The lubricating oil that has passed through the regulating valve 45 and has flowed out of the regulating valve 45 flows through the return flow path 46g and returns to the oil tank 34 again. By operating the third knob 45a, it is possible to adjust the flow rate of the lubricating oil that branches from the filter installation space 46c, flows through the branch flow path 46f, the adjustment valve 45, and the return flow path 46g and returns to the oil tank 34. . If the flow rate of the lubricating oil that passes through the regulating valve 45 and returns to the oil tank 34 increases, the flow rate of the lubricating oil toward the nozzle 35 via the second supply pipe 47 decreases, so the third knob 45a is operated. Thereby, the flow volume of the lubricating oil supplied to the sliding location of the turbo compressor 4 can be adjusted.
The supply operation of the lubricating oil in the supply unit 40 is thus completed.

Since the branching channel 46f and the return channel 46g are opened in the installation part 46e, the branching channel 46f and the return channel with respect to the regulation valve 45 can be provided by installing the regulation valve 45 in the installation unit 46e. All of 46g are directly connected. Therefore, the number of parts such as piping for connecting the adjustment valve 45 to the pump 41 side and the oil tank 34 side can be reduced. By reducing the number of parts such as piping, the assembling work of the supply unit 40 can be simplified and the occurrence of oil leakage can be suppressed.
Further, the lubricating oil that returns to the oil tank 34 via the regulating valve 45 is a lubricating oil that has branched before passing through the oil filter 42. Therefore, the amount of lubricating oil filtered by the oil filter 42 can be suppressed, and the filter life of the oil filter 42 can be extended.

Next, the operation of the turbo compressor 4 in this embodiment will be described.
First, the rotational power of the motor 12 is transmitted to the rotary shaft 23 via the spur gear 31 and the pinion gear 32, whereby the first impeller 21a and the second impeller 22a of the compressor unit 20 are rotationally driven.

 When the first impeller 21a is driven to rotate, the suction port 21d of the first compression stage 21 enters a negative pressure state, and the refrigerant gas X4 flows from the flow path R5 into the first compression stage 21 through the suction port 21d. The refrigerant gas X4 that has flowed into the first compression stage 21 flows into the first impeller 21a from the thrust direction, is given speed energy by the first impeller 21a, and is discharged in the radial direction. The refrigerant gas X4 discharged from the first impeller 21a is compressed by converting velocity energy into pressure energy by the first diffuser 21b. The refrigerant gas X4 discharged from the first diffuser 21b is led out of the first compression stage 21 through the first scroll chamber 21c. Then, the refrigerant gas X4 led out of the first compression stage 21 is supplied to the second compression stage 22 via an external pipe (not shown).

The refrigerant gas X4 supplied to the second compression stage 22 flows into the second impeller 22a from the thrust direction through the introduction scroll chamber 22d, and is discharged in the radial direction to which velocity energy is applied by the second impeller 22a. The refrigerant gas X4 discharged from the second impeller 22a is further compressed into a compressed refrigerant gas X1 by converting velocity energy into pressure energy by the second diffuser 22b. The compressed refrigerant gas X1 discharged from the second diffuser 22b is led out of the second compression stage 22 through the second scroll chamber 22c. Then, the compressed refrigerant gas X1 led out of the second compression stage 22 is supplied to the condenser 1 via the flow path R1.
Thus, the operation of the turbo compressor 4 is completed.

Therefore, according to the present embodiment, the following effects can be obtained.
According to the present embodiment, the number of nozzles, supply pipes, and the like for supplying lubricating oil to the fourth bearing 27 and the meshing portion 38 can be reduced. In the turbo compressor 4 and the turbo refrigerator S1 including the turbo compressor 4, There is an effect that labor and cost can be reduced.

 As described above, the preferred embodiments according to the present invention have been described with reference to the accompanying drawings, but the present invention is not limited to the examples. Various shapes, combinations, and the like of the constituent members shown in the above-described examples are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.

 For example, in the above-described embodiment, both the branch flow path 46f and the return flow path 46g are open to the installation part 46e, but the present invention is not limited to this, and either one is open to the installation part 46e. May be. The effect of reducing the number of parts such as pipes can be obtained only by opening one flow path to the installation portion 46e.

 In the above embodiment, the branch flow path 46f is branched from the filter installation space 46c. However, the present invention is not limited to this, and the flow through which the lubricating oil after being filtered in the oil filter 42 flows. It may be branched from the road.

 Moreover, in the said embodiment, although the installation part 46e is formed in planar shape, what is necessary is just to hold | maintain between the installation part 46e and the adjustment valve 45 liquid-tight, for example, in the installation part 46e, the branch flow path 46f A stepped portion may be provided between the return flow path 46g.

DESCRIPTION OF SYMBOLS 1 ... Condenser, 3 ... Evaporator, 4 ... Turbo compressor, 34 ... Oil tank, 34a ... Opening part, 41 ... Pump, 42 ... Oil filter, 45 ... Adjustment valve, 46 ... Oil tank cover, 46e ... Installation part , 46f: Branch channel (first channel), 46g: Return channel (second channel)

Claims (4)

A turbo provided with a pump for sending lubricating oil stored in an oil tank having an opening, and an adjustment valve for adjusting the flow rate of the lubricating oil branched from the flow of the lubricating oil sent from the pump and returning to the oil tank A compressor,
An oil tank cover that seals the opening and is provided with an installation portion for the regulating valve;
The oil tank cover opens to the installation portion, and a first flow path in which the flow of the lubricating oil fed from the pump branches and flows toward the regulating valve; and opens to the installation portion and the adjustment A turbo compressor comprising at least one of a second flow path through which lubricating oil flows from a valve toward the oil tank. The turbo compressor according to claim 1, wherein
An oil filter that is installed in the oil tank cover and filters the lubricating oil sent out from the pump;
The turbo compressor according to claim 1, wherein the first flow path is branched from a flow path between the pump and the oil filter. The turbo compressor according to claim 1 or 2,
The turbo compressor according to claim 1, wherein the installation part is formed in a planar shape. A condenser that cools and liquefies the compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes heat of vaporization from the object to be cooled, and cools the refrigerant that has evaporated in the evaporator. A turbo chiller comprising a compressor for compressing and supplying to the condenser,
The turbo refrigerator provided with the turbo compressor as described in any one of Claim 1 to 3 as said compressor.

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