U.S. patent application number 16/081612 was filed with the patent office on 2019-03-14 for refrigerator.
This patent application is currently assigned to MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD.. The applicant listed for this patent is MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD.. Invention is credited to Yasushi HASEGAWA, Naoya MIYOSHI, Kenji UEDA.
Application Number | 20190078811 16/081612 |
Document ID | / |
Family ID | 60785295 |
Filed Date | 2019-03-14 |
![](/patent/app/20190078811/US20190078811A1-20190314-D00000.png)
![](/patent/app/20190078811/US20190078811A1-20190314-D00001.png)
![](/patent/app/20190078811/US20190078811A1-20190314-D00002.png)
![](/patent/app/20190078811/US20190078811A1-20190314-D00003.png)
![](/patent/app/20190078811/US20190078811A1-20190314-D00004.png)
United States Patent
Application |
20190078811 |
Kind Code |
A1 |
MIYOSHI; Naoya ; et
al. |
March 14, 2019 |
REFRIGERATOR
Abstract
The purpose of the present invention is to provide a
refrigerator in which the capacity of an oil tank can be made
smaller than in the prior art while a foaming phenomenon is
addressed. The refrigerator is provided with: a refrigeration cycle
which includes a condenser, an evaporator, and an electric
compressor having a compression mechanism to be driven by a motor
and in which a refrigerant circulates; an oil tank in which a
lubricating oil is stored; a heater which is set in the oil tank
and which heats the lubricating oil; a lubricating oil supply line
which is connected to the oil tank and which supplies the
lubricating oil from the oil tank into a housing having the motor
housed therein; a lubricating oil discharge line which returns the
lubricating oil from the housing back to the oil tank; a pressure
equalizing pipe which has one end connected to the oil tank and the
other end connected to the refrigeration cycle; and a buffer tank
which is set to the pressure equalizing pipe, which receives the
refrigerant and the lubricating oil flowing out from the oil tank,
and in which the lubricating oil is stored.
Inventors: |
MIYOSHI; Naoya; (Tokyo,
JP) ; UEDA; Kenji; (Tokyo, JP) ; HASEGAWA;
Yasushi; (Tokyo, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. |
Tokyo |
|
JP |
|
|
Assignee: |
MITSUBISHI HEAVY INDUSTRIES THERMAL
SYSTEMS, LTD.
Tokyo
JP
|
Family ID: |
60785295 |
Appl. No.: |
16/081612 |
Filed: |
June 26, 2017 |
PCT Filed: |
June 26, 2017 |
PCT NO: |
PCT/JP2017/023420 |
371 Date: |
August 31, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 2700/21155
20130101; F25B 2400/01 20130101; F25B 1/10 20130101; F25B 31/026
20130101; F25B 2500/16 20130101; F25B 2400/13 20130101; F25B 40/02
20130101; F25B 31/008 20130101; F25B 43/02 20130101; F25B 1/04
20130101; F25B 31/004 20130101 |
International
Class: |
F25B 1/04 20060101
F25B001/04; F25B 1/10 20060101 F25B001/10; F25B 31/00 20060101
F25B031/00; F25B 31/02 20060101 F25B031/02 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 30, 2016 |
JP |
2016-130103 |
Claims
1. A chiller comprising: a refrigerating cycle that includes an
electric compressor having a compression mechanism driven by a
motor, a condenser, and an evaporator, and in which a refrigerant
is circulated; an oil tank that stores a lubricant; a heater that
is installed inside the oil tank so as to heat the lubricant; an
oil circulation pipe that is connected to the oil tank so as to
supply the lubricant from the oil tank into a housing for
accommodating the motor and to return the lubricant from the
housing to the oil tank; a pressure equalizing pipe, one end of
which is connected to the oil tank, separately from the oil
circulation pipe, and the other end of which is connected to the
refrigerating cycle; and a buffer tank that is installed in the
pressure equalizing pipe, and that receives the refrigerant and the
lubricant which flow out of the oil tank so as to store the
lubricant.
2. The chiller according to claim 1, further comprising: a return
pipe, one end of which is connected to the buffer tank, and the
other end of which is connected to the oil tank, separately from
the pressure equalizing pipe, and that returns the lubricant stored
in the buffer tank to the oil tank.
3. The chiller according to claim 2, wherein a position where the
return pipe is connected to the oil tank is in the vicinity of a
position where the oil circulation pipe is connected to the oil
tank.
4. The chiller according to claim 1, wherein the oil tank is
partitioned by a partition plate, and is divided into a separation
region into which the lubricant returned from the housing flows,
and a discharge region through which the lubricant is supplied to
the housing.
5. The chiller according to claim 4, wherein a flow forming plate
for guiding a flow of the lubricant stored in the oil tank from an
upper portion toward a lower portion or from the lower portion
toward the upper portion is installed in the separation region.
6. The chiller according to claim 4, wherein the partition plate is
installed away from a bottom surface of the oil tank.
7. The chiller according to claim 2, wherein the oil tank is
partitioned by a partition plate, and is divided into a separation
region into which the lubricant returned from the housing flows,
and a discharge region through which the lubricant is supplied to
the housing.
8. The chiller according to claim 7, wherein a flow forming plate
for guiding a flow of the lubricant stored in the oil tank from an
upper portion toward a lower portion or from the lower portion
toward the upper portion is installed in the separation region.
9. The chiller according to claim 7, wherein the partition plate is
installed away from a bottom surface of the oil tank.
10. The chiller according to claim 3, wherein the oil tank is
partitioned by a partition plate, and is divided into a separation
region into which the lubricant returned from the housing flows,
and a discharge region through which the lubricant is supplied to
the housing.
11. The chiller according to claim 10, wherein a flow forming plate
for guiding a flow of the lubricant stored in the oil tank from an
upper portion toward a lower portion or from the lower portion
toward the upper portion is installed in the separation region.
12. The chiller according to claim 10, wherein the partition plate
is installed away from a bottom surface of the oil tank.
Description
TECHNICAL FIELD
[0001] The present invention relates to a chiller.
BACKGROUND ART
[0002] A turbo compressor installed in a centrifugal chiller is
configured to include a compression mechanism and an acceleration
mechanism. In order to stably operate the turbo compressor, it is
necessary to properly and continuously supply a lubricant to a
bearing for supporting an impeller of the compression mechanism or
a gear of the acceleration mechanism. A lubricant system includes
an oil tank and an oil pump. The lubricant stored in the oil tank
is supplied to the bearing or the gear of the turbo compressor by
the oil pump. The lubricant supplied to the bearing or the gear is
returned to the oil tank so as to be repeatedly circulated in the
lubricant system.
[0003] In the compression mechanism, the refrigerant system and the
lubricant system are not completely independent of each other.
Accordingly, the refrigerant dissolves in the lubricant. If the
refrigerant dissolves in the lubricant, viscosity decreases. Thus,
in order to reduce the dissolving amount of the refrigerant in the
oil tank, the oil tank is internally maintained at low pressure.
Therefore, for example, a pressure equalizing pipe communicating
with a low pressure portion (for example, an evaporator or a
compressor suction port) of the refrigerant system is connected to
the oil tank.
[0004] PTL 1 below discloses a technique as follows. When the
centrifugal chiller is started, the pressure inside the oil tank is
lowered, and the refrigerant dissolving in the lubricant is
gasified to cause foaming. Accordingly, a target opening degree is
provided for a suction capacity control unit for controlling
capacity of the refrigerant passing through that the turbo
compressor when the centrifugal chiller is started. In addition,
PTL 2 below discloses a technique as follows. The other end of the
pressure equalizing pipe whose one end is connected to the oil tank
is connected to an economizer instead of the evaporator so that the
internal pressure of the oil tank and the internal pressure of the
economizer are equalized.
CITATION LIST
Patent Literature
[0005] [PTL 1] Japanese Unexamined Patent Application Publication
No. 2009-186030
[0006] [PTL 2] Japanese Unexamined Patent Application Publication
No. 2009-293901
SUMMARY OF INVENTION
Technical Problem
[0007] The internal pressure is lowered in the oil tank
communicating with the refrigerant system, when the centrifugal
chiller in which the pressure of the refrigerant system is lowered
starts to be operated or is in a transition stage. Here, the
transition stage means a time at which an operation state is
changed, for example, such as a case of lowering an output of the
centrifugal chiller. If the internal pressure of the lubricant
system is lowered, such as in a case where the internal pressure of
the oil tank is lowered, the refrigerant dissolving in the
lubricant no longer dissolves beyond a saturated state, and
refrigerant gas is generated, thereby causing a foaming phenomenon
in which the lubricant forms bubbles.
[0008] Inside the oil tank where the foaming phenomenon occurs, the
oil level rises, compared to a normal time during which the foaming
phenomenon does not occur. In addition, if the foaming phenomenon
occurs, the supply amount of the lubricant which can be supplied to
a bearing or a gear is reduced in the lubricant system. In a case
of a low pressure refrigerant (for example, R1233zd), a refrigerant
gas specific volume is larger than that of a high pressure
refrigerant (for example, R134a). Accordingly, a large volume of
the gas is generated during the foaming phenomenon. Therefore, in a
case of the low pressure refrigerant, when the oil level rises or
the supply amount of the lubricant is reduced, there is a greater
difference, compared to the normal time.
[0009] The pressure equalizing pipe connected to the oil tank is
connected to an upper portion of the oil tank. However, the
lubricant having the foaming is caused to flow into the pressure
equalizing pipe due to the oil level rising during the foaming,
thereby causing a possibility that the lubricant may flow to the
evaporator which is a connecting destination of the pressure
equalizing pipe. Therefore, in the related art, in order to cope
with the oil level rising during the foaming, a height of the oil
tank is increased.
[0010] In addition, while a depth of the oil tank is increased, and
the oil pump is located on a bottom surface of the oil tank so that
the oil pump does not suction the refrigerant gas during the
foaming. In this manner, the oil level when the foaming occurs and
a position of the oil pump are separated from each other.
[0011] In any case, it is necessary to increase a size of the oil
tank in a height direction, and the large capacity of the oil tank
has to be set in order to cope with the foaming phenomenon.
[0012] The present invention is made in view of the above-described
circumstances, and an object thereof is to provide a chiller which
can cope with a foaming phenomenon and can decrease capacity of an
oil tank, compared to that in the related art.
Solution to Problem
[0013] In order to solve the above-described problems, a chiller
according to the present invention adopts the following means.
[0014] That is, according to the present invention, there is
provided a chiller including a refrigerating cycle that includes an
electric compressor having a compression mechanism driven by a
motor, a condenser, and an evaporator, and in which a refrigerant
is circulated, an oil tank that stores a lubricant, a heater that
is installed inside the oil tank so as to heat the lubricant, an
oil circulation pipe that is connected to the oil tank so as to
supply the lubricant from the oil tank into a housing for
accommodating the motor and to return the lubricant from the
housing to the oil tank, a pressure equalizing pipe, one end of
which is connected to the oil tank, separately from the oil
circulation pipe, and the other end of which is connected to the
refrigerating cycle, and a buffer tank that is installed in the
pressure equalizing pipe, and that receives the refrigerant and the
lubricant which flow out of the oil tank so as to store the
lubricant.
[0015] According to this configuration, the motor for driving the
compression mechanism is accommodated in the housing, and the
lubricant is supplied from the oil tank to the housing.
Accordingly, a bearing for supporting a rotary shaft of the motor
can be lubricated with the lubricant. In addition, one end of the
pressure equalizing pipe is connected to the oil tank, and the
other end of the pressure equalizing pipe is connected to the
refrigerating cycle. Therefore, pressure of a portion connected to
the refrigerating cycle and internal pressure of the oil tank are
substantially equalized. A portion to which the pressure equalizing
pipe is connected in the refrigerating cycle is a portion where the
pressure is low in the refrigerating cycle, for example, such as an
evaporator and a compressor suction port.
[0016] Furthermore, the refrigerant and the lubricant which flow
out of the oil tank are supplied to the buffer tank via the
pressure equalizing pipe, and are temporarily stored in the buffer
tank. In this manner, even if foaming occurs inside the oil tank
and the refrigerant and the lubricant flow out of the oil tank, the
lubricant is stored in the buffer tank, and does not flow to the
refrigerating cycle. Accordingly, only the refrigerant is guided
toward the refrigerating cycle.
[0017] In the above-described invention, the chiller may further
include a return pipe, one end of which is connected to the buffer
tank, and the other end of which is connected to the oil tank,
separately from the pressure equalizing pipe, and that returns the
lubricant stored in the buffer tank to the oil tank.
[0018] According to this configuration, one end of the return pipe
is connected to the buffer tank, and the other end of the return
pipe is connected to the oil tank so that the lubricant stored in
the buffer tank is returned to the oil tank. In this manner, the
lubricant flowing out of the oil tank and accumulated in the buffer
tank is returned to the oil tank without flowing into the
refrigerant cycle.
[0019] In the above-described invention, a position where the
return pipe is connected to the oil tank may be located on a side
close to a position where the oil circulation pipe is connected to
the oil tank.
[0020] According to this configuration, the lubricant returned from
the buffer tank is returned to the vicinity of the position where
the oil circulation pipe is connected to the oil tank. Accordingly,
even in a case where the foaming occurs inside the oil inside the
oil tank 23, the lubricant returned from the buffer tank is mixed
with the lubricant which is not affected by the foaming.
[0021] In the above-described invention, the oil tank may be
partitioned by a partition plate, and may be divided into a
separation region into which the lubricant returned from the
housing flows, and a discharge region through which the lubricant
is supplied to the housing.
[0022] According to this configuration, the lubricant having the
dissolved refrigerant is supplied to the separation region, and the
lubricant having the dissolved refrigerant is separated into the
lubricant and the refrigerant in the separation region. Then, the
separated lubricant is supplied from the separation region to the
discharge region, and is supplied into the housing. The separation
region and the discharge region are partitioned by the partition
plate. Accordingly, in the separation region, the lubricant flowing
into the oil tank is efficiently separated using a difference
between the lubricant and the refrigerant or an enclosed space. In
addition, even if the foaming phenomenon occurs in the separation
region, it is possible to prevent the lubricant having the bubbles
formed therein from flowing into the discharge region.
[0023] In the above-described invention, a flow forming plate for
guiding a flow of the lubricant stored in the oil tank from an
upper portion toward a lower portion or from the lower portion
toward the upper portion may be installed in the separation
region.
[0024] According to this configuration, it is possible to form a
flow guided from the upper portion toward the lower portion inside
the stored lubricant, or conversely to form a flow guided from the
lower portion toward the upper portion.
[0025] In the above-described invention, the partition plate may be
installed away from a bottom surface of the oil tank.
[0026] According to this configuration, the lubricant having the
dissolved refrigerant flows to a downstream side without staying in
a bottom portion inside the separation region.
Advantageous Effects of Invention
[0027] According to the present invention, it is possible to cope
with a foaming phenomenon and to decrease capacity of an oil tank,
compared to that in the related art.
BRIEF DESCRIPTION OF DRAWINGS
[0028] FIG. 1 is a configuration diagram illustrating a centrifugal
chiller according to an embodiment of the present invention.
[0029] FIG. 2 is a longitudinal sectional view illustrating a turbo
compressor of the centrifugal chiller according to the embodiment
of the present invention.
[0030] FIG. 3 is a perspective view illustrating an oil tank of the
centrifugal chiller according to the embodiment of the present
invention.
[0031] FIG. 4 is a perspective view illustrating a modification
example of the oil tank of the centrifugal chiller according to the
embodiment of the present invention.
DESCRIPTION OF EMBODIMENTS
[0032] Hereinafter, a centrifugal chiller 1 according to an
embodiment of the present invention will be described with
reference to the drawings.
[0033] As illustrated in FIG. 1, the centrifugal chiller 1 includes
a turbo compressor 2 which compresses a refrigerant, a condenser 3
which cools and condenses the refrigerant, a sub-cooler 4 which
re-cools and applies super-cooling to the refrigerant condensed in
the condenser 3, a first pressure-reducing valve 5 which reduces
pressure of a high pressure refrigerant to be intermediate
pressure, an economizer 6 which applies the super-cooling to the
refrigerant, a second pressure-reducing valve 7 which reduces the
pressure of the refrigerant to be low pressure, and an evaporator 8
which evaporates a low pressure refrigerant.
[0034] The turbo compressor 2, the condenser 3, the sub-cooler 4,
the first pressure-reducing valve 5, the economizer 6, the second
pressure-reducing valve 7, and the evaporator 8 configure a
refrigerating cycle. The refrigerant is circulated in order of the
turbo compressor 2, the condenser 3, the sub-cooler 4, the first
pressure-reducing valve 5, the economizer 6, the second
pressure-reducing valve 7, and the evaporator 8. The refrigerant is
supplied from the economizer 6 to the turbo compressor 2 using a
bypass without passing through the evaporator 8.
[0035] The turbo compressor 2 includes a housing 30 configured so
that a motor housing 31, an accelerator housing 32, and a
compressor housing 33 are combined integrally with each other.
[0036] As illustrated in FIG. 2, a motor 9 driven so that variable
speed is allowed by an inverter device is incorporated in the motor
housing 31. One end 10a of the motor shaft 10 of the motor 9
protrudes from the motor housing 31 to the accelerator housing 32.
The motor 9 includes a stator 20 and a rotor 21. The rotor 21 is
fixed to the motor shaft 10, and the rotor 21 is rotated inside the
stator 20. The motor shaft 10 is supported by the rolling bearing
14 on the side of the accelerator housing 32. The rolling bearing
14 has a plurality of angular ball bearings, for example. The
rolling bearing 14 is installed in the motor housing 31 via a
bearing box (not illustrated).
[0037] The compressor housing 33 internally accommodates a
compression mechanism 15 having a first stage compression stage and
a second stage compression stage. The refrigerant suctioned into
the first stage compression stage from the outside and compressed
by the first stage compression stage is supplied to the second
stage compression stage. Then, the refrigerant, suctioned into the
second stage compression stage and compressed by the second stage
compression stage is discharged outward.
[0038] A rotary shaft 11 is rotatably installed inside the
compressor housing 33. One end 11a side of the rotary shaft 11 has
a first stage impeller 12 for the first stage compression stage and
a second stage impeller 13 for the second stage compression stage.
The rotary shaft 11 is supported by a rolling bearing 14 on a side
of the accelerator housing 32. For example, the rolling bearing 14
includes a plurality of angular ball bearings. The rolling bearing
14 is installed in the compressor housing 33 via a bearing box (not
illustrated).
[0039] The other end 11b side of the rotary shaft 11 supported by
the rolling bearing 14 has a small diameter gear 17. The gear 17
meshes with a large diameter gear 18 disposed in one end 10a of the
motor shaft 10. These gears 17 and 18 configure an acceleration
mechanism 19. The acceleration mechanism 19 is accommodated in the
accelerator housing 32.
[0040] In the rolling bearing 14 and the gears 17 and 18, a
lubricant is supplied to each component.
[0041] A lubricant system is configured to include a lubricant
supply line 22 and a lubricant discharge line 25.
[0042] The lubricant supply line 22 is a pipe for connecting the
oil tank 23 and the turbo compressor 2 to each other. The lubricant
is supplied from the oil tank 23 to the motor housing 31 of the
turbo compressor 2 and the accelerator housing 32 by an oil pump 36
disposed in the lubricant supply line 22. The lubricant passing
through the motor 9 and the acceleration mechanism 19 is returned
to the oil tank 23 via the lubricant discharge line 25. An oil
cooler 24 is installed in the lubricant supply line 22 and the
lubricant discharge line 25 according to the present
embodiment.
[0043] The motor housing 31 and the accelerator housing 32 have
each lubricant inlet connected to the lubricant supply line 22, and
the lubricant is supplied from the lubricant supply line 22 to the
turbo compressor 2. The refrigerant extracted from the condenser 3
which configures the refrigerating cycle is supplied to the turbo
compressor 2. The motor housing 31 and the accelerator housing 32
have each liquid refrigerant inlet connected to a refrigerant
supply line 34, and a liquid refrigerant is supplied from the
refrigerant supply line 34.
[0044] The lubricant passing through the inside of the motor
housing 31 and the inside of the accelerator housing 32 of the
turbo compressor 2 is discharged to the oil tank 23. The motor
housing 31 and the accelerator housing 32 have each lubricant
outlet connected to the lubricant discharge line 25. The
refrigerant and the lubricant are discharged from the motor housing
31 and the accelerator housing 32 to the oil tank 23 via the
lubricant discharge line 25.
[0045] In the lubricant discharged to the oil tank 23, the
refrigerant dissolves, and the lubricant is diluted by the
refrigerant. A heater 27 (refer to FIG. 3) for evaporating the
refrigerant in order to increase concentration of the diluted
lubricant is installed in the oil tank 23. Since the refrigerant is
evaporated, kinematic viscosity of the lubricant returns to a state
before the lubricant is diluted. Thus, the lubricant can be
repeatedly used as the lubricant for lubricating the gears 17 and
18 and the rolling bearing 14.
[0046] As illustrated in FIG. 3, the oil tank 23 is a container
capable of accommodating the lubricant, and the lubricant is stored
in a lower portion inside the oil tank 23.
[0047] The oil tank 23 can be roughly divided into a separation
region 41 and a discharge region 42.
[0048] The oil tank 23 has a lubricant and refrigerant inlet
connected to the lubricant discharge line 25. For example, the
heater 27 is installed in a lower portion of the separation region
41 of the oil tank 23. The refrigerant and the lubricant inside the
oil tank 23 are heated so as to evaporate the refrigerant. In this
manner, refrigerant gas generated by evaporation is guided upward
of the oil tank 23, and the lubricant having reduced content of the
refrigerant after the refrigerant evaporates flows to a downstream
side of the oil tank 23.
[0049] A lubricant outlet connected to the lubricant supply line 22
is formed below the oil tank 23. According to the present
embodiment, the oil pump 36 is installed in the lubricant outlet.
The lubricant is supplied from the oil tank 23 to the turbo
compressor 2 via the lubricant supply line 22.
[0050] In addition, a refrigerant gas outlet connected to the
pressure equalizing pipe 29 is formed above the oil tank 23, and
the refrigerant gas is supplied from the oil tank 23 to the
evaporator 8 via the pressure equalizing pipe 29. In this manner,
the refrigerant supplied to the turbo compressor 2 from the
condenser 3 and the sub-cooler 4 is returned to the refrigerating
cycle.
[0051] In addition, one end of the pressure equalizing pipe 29 is
connected to the oil tank 23, and the other end of the pressure
equalizing pipe 29 is connected to the evaporator 8 of the
refrigerating cycle. Accordingly, pressure of the evaporator 8 in a
portion connected to the refrigerating cycle and internal pressure
of the oil tank 23 are substantially equalized. A connecting
destination of the pressure equalizing pipe 29 is not limited to
the evaporator 8, and may be a suction port of the turbo compressor
2, for example.
[0052] It is preferable to adjust the lubricant stored inside the
oil tank 23 so as to maintain a predetermined temperature range.
For example, the temperature of the lubricant is determined, based
on the temperature at which adequate lubrication can be achieved in
the gears 17 and 18 and the rolling bearing 14 in the turbo
compressor 2 lubricated with the lubricant.
[0053] The temperature of the lubricant stored inside the oil tank
23 is adjusted, for example, by means of heating using the heater
27. The heating using the heater 27 is controlled by the
temperature measured by a temperature measuring unit 35 installed
in a lower portion of the oil tank 23. Based on the measured
temperature, turning on and off of the heater 27 may be controlled
so as to adjust the heating of the refrigerant or the lubricant.
Alternatively, based on the measured temperature, the setting
temperature of the heater 27 may be adjusted.
[0054] The oil tank 23 is partitioned by a partition plate 43, and
is divided into the separation region 41 and the discharge region
42. The partition plate 43 is a plate-shaped member, and a side end
portion is in contact with an inner surface of the oil tank 23. In
this manner, the oil tank 23 is divided into two regions by the
partition plate 43 serving as a boundary. The lubricant discharge
line 25 side from the partition plate 43 is the separation region
41 into which the lubricant returned from the housing 30 flows. In
addition, the lubricant supply line 22 side from the partition
plate 43 is the discharge region 42 through which the lubricant is
supplied to the housing 30.
[0055] The lubricant having the dissolved refrigerant is supplied
from the lubricant discharge line 25 to the separation region 41.
The lubricant having the dissolved refrigerant has higher specific
gravity than that of the refrigerant alone and the lubricant alone.
The concentration is high on a bottom surface of the separation
region 41. The refrigerant is heated and gasified by the heater 27
located close to the bottom surface of the separation region 41
having the high concentration of the refrigerant, and the lubricant
having the dissolved refrigerant is separated into the lubricant
and the refrigerant. Inside the oil tank 23, a space for storing
the lubricant is limited by the partition plate 43. Accordingly,
the lubricant can be efficiently heated by the heater 27.
[0056] The separation region 41 may have a plurality of flow
forming plates 44 other than the above-described partition plate
43. The flow forming plates 44 are installed in the separation
region 41. In this way, inside the stored lubricant, it is possible
to form a flow in which the lubricant is guided from an upper
portion to a lower portion, or conversely to form a flow in which
the lubricant is guided from the lower portion to the upper
portion. In this manner, the lubricant can be efficiently brought
into contact with the heater 27, or the separated and gasified
refrigerant can be raised upward.
[0057] The heated and gasified refrigerant rises upward of the
lubricant stored in the oil tank 23. Even in a case where a foaming
phenomenon occurs, the lubricant having bubbles formed therein
rises along the partition plate 43 or the flow forming plate 44.
Thereafter, the bubbles are in a state of floating on the liquid
lubricant. Therefore, according to the present embodiment, unlike a
case where the partition plate 43 and the flow forming plate 44 are
not provided, the bubbles formed by the refrigerant gas are less
likely to flow to the downstream side inside the liquid lubricant.
As a result, the bubbles can be prevented from being suctioned into
the oil tank 23.
[0058] The lubricant stored inside the oil tank 23 is caused to
flow in one direction by the oil pump 36, that is, to flow from the
lubricant and refrigerant inlet side to the lubricant outlet side.
In this manner, the lubricant whose refrigerant concentration is
lowered by separating the refrigerant flows toward the lubricant
outlet side. In addition, in a case where the foaming phenomenon
occurs, the bubbles floating on the lubricant also flows toward the
downstream side along the flow of the lubricant.
[0059] If the oil level is raised by the bubbles due to the foaming
phenomenon, the bubbles pass through the inside of the pressure
equalizing pipe 29, and the foamy lubricant falls into the buffer
tank 28.
[0060] A lower end portion of the partition plate 43 or the flow
forming plate 44 may be in contact with the bottom surface of the
oil tank 23, or may be located away from the bottom surface. In a
case where the lower end portion is in contact with the bottom
surface, a flow from the lower portion to the upper portion is
formed in the lubricant. In a case where the lower end portion is
located away from the bottom surface, the lubricant having the
dissolved refrigerant flows to the downstream side without staying
in the bottom portion inside the separation region 41. In this
case, the lubricant having the dissolved refrigerant flows along
the heater 27. Accordingly, the refrigerant can be efficiently
gasified.
[0061] In addition, in the example illustrated in FIG. 3, a case of
installing one partition plate 43 and two flow forming plates 44 is
illustrated. However, the present invention is not limited to this
example. For example, as illustrated in FIG. 4, one partition plate
43 and one flow forming plate 44 may be installed.
[0062] The oil pump 36 is installed in the discharge region 42. For
example, the oil pump 36 is an immersion pump, and is installed on
the bottom surface of the oil tank 23. The oil pump 36 suctions the
lubricant in the bottom portion of the oil tank 23, and supplies
the lubricant to the outside, that is, to the housing 30. According
to the present embodiment, in a case where the foaming phenomenon
occurs, the bubble rises in the separation region 41. Therefore,
the oil pump 36 installed in the discharge region 42 is less likely
to suction the refrigerant gas.
[0063] The heater 27 may be installed in only the separation region
41 on the upstream side, or may also be installed in the discharge
region 42 on the downstream side as illustrated in FIG. 3. Since
the heater 27 is installed in the discharge region 42, it is
possible to increase the amount of the refrigerant separated from
the lubricant. However, in a case where the foaming phenomenon may
possibly occur due to the heating using the heater 27 in the
discharge region 42, it is preferable not to install the heater 27
in the discharge region 42.
[0064] The buffer tank 28 is installed in the pressure equalizing
pipe 29. The buffer tank 28 can store the foamy lubricant flowing
out of the oil tank 23, and has capacity not to allow the lubricant
to flow out to the pressure equalizing pipe 29 on the downstream
side. An upper portion of the buffer tank 28 has an inlet portion
connected to the pressure equalizing pipe 29 connected with the oil
tank 23. In addition, the upper portion of the buffer tank 28 has
an outlet portion formed at a portion separate from the inlet
portion. The outlet portion is connected to the pressure equalizing
pipe 29 connected to the evaporator 8.
[0065] The refrigerant and the lubricant which flow out of the oil
tank 23 are supplied to the buffer tank 28 via the pressure
equalizing pipe 29. Then, the lubricant flowing out of the oil tank
23 is temporarily stored in the buffer tank 28. In addition, the
gasified refrigerant dissolving in the lubricant flows from the
buffer tank 28 to the evaporator 8.
[0066] In this manner, even if the foaming occurs inside the oil
tank 23 and the foamy refrigerant and lubricant flow out of the oil
tank 23, the lubricant is stored in the buffer tank 28, and does
not flow to the refrigerating cycle. Only the refrigerant is guided
to the refrigerating cycle.
[0067] The return pipe 26 is connected to below the oil tank 23. In
the return pipe 26, for example, one end is connected to the bottom
surface of the buffer tank 28, and the other end is connected to
the oil tank 23. The return pipe 26 is disposed separately from the
pressure equalizing pipe 29, and returns the lubricant stored in
the buffer tank 28 to the oil tank 23. In this manner, the
lubricant flowing out of the oil tank 23 and accumulated in the
buffer tank 28 is returned to the oil tank 23 without flowing to
the refrigerant cycle.
[0068] A position where the return pipe 26 is connected to the oil
tank 23 is located on a side close to a position where the
lubricant supply line 22 is connected to the oil tank 23. In this
manner, the lubricant returned from the buffer tank 28 is returned
to the vicinity of the position where the lubricant supply line 22
is connected to the oil tank 23, for example, to the discharge
region 42. Accordingly, the lubricant returned from the buffer tank
28 is mixed with the lubricant which is not affected by the
foaming, even in a case where the foaming occurs inside the oil
tank 23.
[0069] Next, a supply method and a cooling method of the lubricant
in the centrifugal chiller 1 according to the present embodiment
will be described.
[0070] The lubricant is stored in the oil tank 23, and is supplied
from the oil tank 23 to the turbo compressor 2 by the oil pump 36.
The lubricant supplied to the turbo compressor 2 is supplied to the
gears 17 and 18 and the rolling bearing 14 inside the motor housing
31 of the turbo compressor 2 and inside the accelerator housing
32.
[0071] While the lubricant supplied to the gears 17 and 18 and the
rolling bearing 14 is used in lubricating the gears 17 and 18 and
the rolling bearing 14, the temperature of the lubricant rises due
to a friction loss.
[0072] The lubricant passing through the motor housing 31 and the
accelerator housing 32 of the turbo compressor 2 is cooled after
passing through the oil cooler 24. In this manner, the lubricant
passing through the gears 17 and 18 and the rolling bearing 14
inside the motor housing 31 and the accelerator housing 32 of the
turbo compressor 2 is cooled by the oil cooler 24.
[0073] Thereafter, the lubricant cooled by the oil cooler 24 and
the refrigerant dissolving in the lubricant are discharged to the
oil tank 23.
[0074] The lubricant and the refrigerant which are discharged to
the oil tank 23 flows to the lower portion in the separation region
41, and is heated by the heater 27 installed in the lower portion
inside the oil tank 23 so that the refrigerant evaporates. As a
result, the kinematic viscosity of the lubricant diluted by the
refrigerant is recovered.
[0075] The lubricant having reduced content of the refrigerant
after the refrigerant evaporates flows to the downstream side of
the oil tank 23. In addition, the refrigerant gas evaporated by the
heater 27 is guided upward of the oil tank 23. The refrigerant gas
is supplied from the oil tank 23 to the evaporator 8 through the
pressure equalizing pipe 29 and the buffer tank 28.
[0076] In a case of the foaming phenomenon where the pressure
inside the oil tank 23 is lowered due to the lowered pressure in
the refrigerating cycle and the refrigerant forms the bubbles due
to the gasified lubricant, the bubbles formed by the refrigerant
and the lubricant rise along the partition plate 43 or the flow
forming plate 44. Furthermore, the bubbles floating on the liquid
lubricant flow toward the downstream side along the flow of the
lubricant.
[0077] If the oil level is raised by the bubbles due to the foaming
phenomenon, the bubbles pass through the inside of the pressure
equalizing pipe 29, and the bubbles formed by the refrigerant and
the lubricant fall into the buffer tank 28. As a result, the
lubricant is stored in the lower portion inside the buffer tank 28,
and the gasified refrigerant flows to the evaporator 8 via the
pressure equalizing pipe 29.
[0078] As described above, according to the present embodiment, the
refrigerant and the lubricant which flow out of the oil tank 23 are
supplied to the buffer tank 28 via the pressure equalizing pipe 29,
and the lubricant is temporarily stored in the buffer tank 28. In
this manner, even if the foaming occurs inside the oil tank 23 and
the refrigerant and the lubricant flow out of the oil tank 23, the
lubricant is stored in the buffer tank 28, and does not flow to the
refrigerating cycle. Only the refrigerant is guided toward the
refrigerating cycle.
[0079] In addition, the lubricant having the dissolved refrigerant
is supplied to the separation region 41 of the oil tank 23, and the
lubricant having the dissolved refrigerant is separated into the
lubricant and the refrigerant in the separation region 41. Then,
the separated lubricant is supplied from the separation region 41
to the discharge region 42, and is supplied into the housing 30.
The separation region 41 and the discharge region 42 are
partitioned by the partition plate 43. Accordingly, in the
separation region 41, the lubricant flowing into the oil tank 23 is
efficiently separated using a specific gravity difference between
the lubricant and the refrigerant or the increased temperature of
the lubricant in a narrow space. In addition, the partition plate
43 is installed. Accordingly, even if the foaming phenomenon occurs
in the separation region 41, it is possible to prevent the
lubricant having the bubbles formed therein from flowing into the
discharge region 42.
[0080] According to the above-described configurations, it is
possible to reduce the amount of the lubricant flowing out to the
refrigerating cycle such as the evaporator 8. The amount of the
refrigerant suctioned by the oil pump 36 is reduced. Therefore, it
is possible to prevent the amount of the lubricant circulating in
the lubricant system from being reduced.
REFERENCE SIGNS LIST
[0081] 1: centrifugal chiller [0082] 2: turbo compressor [0083] 3:
condenser [0084] 4: sub-cooler [0085] 5: first pressure-reducing
valve [0086] 6: economizer [0087] 7: second pressure-reducing valve
[0088] 8: evaporator [0089] 9: motor [0090] 10: motor shaft [0091]
10a: one end [0092] 11: rotary shaft [0093] 11a: one end [0094]
11b: other end [0095] 12: first stage impeller [0096] 13: second
stage impeller [0097] 14: rolling bearing [0098] 15: compression
mechanism [0099] 17: gear [0100] 18: gear [0101] 19: acceleration
mechanism [0102] 20: stator [0103] 21: rotor [0104] 22: lubricant
supply line [0105] 23: oil tank [0106] 24: oil cooler [0107] 25:
lubricant discharge line [0108] 26: return pipe [0109] 27: heater
[0110] 28: buffer tank [0111] 29: pressure equalizing pipe [0112]
30: housing [0113] 31: motor housing [0114] 32: accelerator housing
[0115] 33: compressor housing [0116] 34: refrigerant supply line
[0117] 35: temperature measuring unit [0118] 36: oil pump [0119]
41: separation region [0120] 42: discharge region [0121] 43:
partition plate [0122] 44: flow forming plate
* * * * *