U.S. patent application number 13/074310 was filed with the patent office on 2011-10-06 for turbo compressor and turbo refrigerator.
Invention is credited to Kazuaki KURIHARA, Kentarou ODA, Noriyasu SUGITANI, Nobusada TAKAHARA, Minoru TSUKAMOTO.
Application Number | 20110243710 13/074310 |
Document ID | / |
Family ID | 44696100 |
Filed Date | 2011-10-06 |
United States Patent
Application |
20110243710 |
Kind Code |
A1 |
KURIHARA; Kazuaki ; et
al. |
October 6, 2011 |
TURBO COMPRESSOR AND TURBO REFRIGERATOR
Abstract
A turbo compressor is provided including: a pump which sends
lubricant stored in an oil tank having an open portion; and a
control valve which adjusts the flow rate of the lubricant
returning to the oil tank by dividing the stream of the lubricant
sent from the pump; and an oil tank cover which blocks the open
portion and is provided with an installation portion for the
control valve, wherein the oil tank cover includes at least one of
a first passage opened from the installation portion and allowing
the stream of the lubricant sent from the pump to be divided and
flow toward the control valve and a second passage opened from the
installation portion and allowing the lubricant to flow from the
control valve toward the oil tank.
Inventors: |
KURIHARA; Kazuaki;
(Yokohama-shi, JP) ; SUGITANI; Noriyasu;
(Yokohama-shi, JP) ; ODA; Kentarou; (Yokohama-shi,
JP) ; TAKAHARA; Nobusada; (Kamiina-gun, JP) ;
TSUKAMOTO; Minoru; (Yokohama-shi, JP) |
Family ID: |
44696100 |
Appl. No.: |
13/074310 |
Filed: |
March 29, 2011 |
Current U.S.
Class: |
415/110 |
Current CPC
Class: |
F04D 25/04 20130101;
F04D 29/063 20130101; F04D 25/06 20130101 |
Class at
Publication: |
415/110 |
International
Class: |
F04D 29/06 20060101
F04D029/06 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 31, 2010 |
JP |
P2010-081123 |
Claims
1. A turbo compressor comprising: a pump which sends lubricant
stored in an oil tank having an open portion; a control valve which
adjusts the flow rate of the lubricant returning to the oil tank by
dividing the stream of the lubricant sent from the pump; and an oil
tank cover which blocks the open portion and is provided with an
installation portion for the control valve, wherein the oil tank
cover includes at least one of a first passage opened from the
installation portion and allowing the stream of the lubricant sent
from the pump to be divided and flow toward the control valve and a
second passage opened from the installation portion and allowing
the lubricant to flow from the control valve toward the oil
tank.
2. The turbo compressor according to claim 1, further comprising:
an oil filter which is provided at the oil tank cover and filters
the lubricant sent from the pump, wherein the first passage is
provided to be divided from the passage between the pump and the
oil filter.
3. The turbo compressor according to claim 1, wherein the
installation portion is formed in a planar shape.
4. The turbo compressor according to claim 2, wherein the
installation portion is formed in a planar shape.
5. A turbo refrigerator comprising: a condenser which cools and
liquefies a compressed refrigerant; an evaporator which evaporates
the liquefied refrigerant and takes evaporation heat from a cooling
object to cool the cooling object; and a compressor which
compresses the refrigerant evaporated from the evaporator and
supplies the compressed refrigerant to the condenser, wherein the
turbo compressor according to claim 1 is used as the
compressor.
6. A turbo refrigerator comprising: a condenser which cools and
liquefies a compressed refrigerant; an evaporator which evaporates
the liquefied refrigerant and takes evaporation heat from a cooling
object to cool the cooling object; and a compressor which
compresses the refrigerant evaporated from the evaporator and
supplies the compressed refrigerant to the condenser, wherein the
turbo compressor according to claim 2 is used as the
compressor.
7. A turbo refrigerator comprising: a condenser which cools and
liquefies a compressed refrigerant; an evaporator which evaporates
the liquefied refrigerant and takes evaporation heat from a cooling
object to cool the cooling object; and a compressor which
compresses the refrigerant evaporated from the evaporator and
supplies the compressed refrigerant to the condenser, wherein the
turbo compressor according to any one of claim 3 is used as the
compressor.
8. A turbo refrigerator comprising: a condenser which cools and
liquefies a compressed refrigerant; an evaporator which evaporates
the liquefied refrigerant and takes evaporation heat from a cooling
object to cool the cooling object; and a compressor which
compresses the refrigerant evaporated from the evaporator and
supplies the compressed refrigerant to the condenser, wherein the
turbo compressor according to claim 4 is used as the compressor.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to a turbo compressor and a
turbo refrigerator.
[0003] Priority is claimed on Japanese Patent Application No.
2010-081123, filed Mar. 31, 2010, the content of which is
incorporated herein by reference.
[0004] 2. Description of Related Art
[0005] Hitherto, as a refrigerator cooling or freezing a cooling
object such as water, a turbo refrigerator has been known including
a turbo compressor compressing a refrigerant through the rotation
of an impeller and discharging the compressed refrigerant. The
turbo compressor included in the turbo refrigerator includes
sliding positions for bearings or gears sliding on the
corresponding members with an operation of a drive unit such as a
motor. Accordingly, for example, as disclosed in Patent Document 1
(Japanese Patent Application First Publication, No. 2009-257684),
the turbo compressor includes a lubricant supply structure which
supplies a lubricant for lubricating the sliding positions. The
lubricant supply structure includes an oil tank which stores the
lubricant and a pump sending the lubricant toward the sliding
positions.
[0006] The lubricant supply structure may include a control valve
that adjusts the flow rate of the lubricant supplied to the sliding
positions. For example, the control valve is installed in a passage
dividing the stream of the lubricant sent from the pump and
returning to the oil tank.
[0007] However, since a plurality of pipes are provided between the
pump and the control valve and between the control valve and the
oil tank to connect them to each other, a problem arises in that
the number of components, such as pipes, increases. Since the
number of components increases, it becomes complicated to assemble
the lubricant supply structure. Further, oil leaks are apt to occur
at the connection positions of the pipes.
[0008] The present invention has been made in view of such
circumstances, and an object thereof is to provide a turbo
compressor capable of decreasing the number of components connected
to a control valve, and a turbo refrigerator including the turbo
compressor.
SUMMARY OF THE INVENTION
[0009] In order to solve the above-described problems, the present
invention adopts the following configurations.
[0010] A turbo compressor according to the present invention is
provided including: a pump which sends lubricant stored in an oil
tank having an open portion; a control valve which adjusts the flow
rate of the lubricant returning to the oil tank by dividing the
stream of the lubricant sent from the pump; and an oil tank cover
which blocks the open portion and is provided with an installation
portion for the control valve, wherein the oil tank cover includes
at least one of a first passage opened from the installation
portion and allowing the stream of the lubricant sent from the pump
to be divided and flow toward the control valve and a second
passage opened from the installation portion and allowing the
lubricant to flow from the control valve toward the oil tank.
[0011] According to the present invention, since at least one of
the first passage and the second passage is opened from the
installation portion, when the control valve is installed at the
installation portion, at least one of the first passage and the
second passage is directly connected to the control valve.
[0012] Further, the turbo compressor according to the present
invention further includes an oil filter which is provided at the
oil tank cover and filters the lubricant sent from the pump,
wherein the first passage is provided to be divided from the
passage between the pump and the oil filter.
[0013] According to the present invention, the lubricant flowing
through the control valve returns to the oil tank without passing
through the oil filter. For this reason, there are advantages in
that the amount of lubricant filtered at the oil filter may be
suppressed and the durability of the oil filter may be
extended.
[0014] Further, in the turbo compressor according to the present
invention, the installation portion is formed in a planar shape.
According to the aspect of the present invention, there is an
advantage in that the liquid tightness between the installation
portion of the oil tank cover and the control valve may be easily
ensured.
[0015] Further, a turbo refrigerator according to the present
invention is provided including: a condenser which cools and
liquefies a compressed refrigerant; an evaporator which evaporates
the liquefied refrigerant and takes evaporation heat from a cooling
object to cool the cooling object; and a compressor which
compresses the refrigerant evaporated from the evaporator and
supplies the compressed refrigerant to the condenser, wherein the
turbo compressor according to the aspect may be used as the
compressor.
[0016] According to the present invention, the following advantage
may be obtained.
[0017] According to the present invention, since the control valve
is installed at the installation portion, at least one of the first
passage and the second passage is directly connected to the control
valve. Accordingly, in the turbo compressor and the turbo
refrigerator, there is an advantage in that the number of
components, such as pipes, connected to the control valve may be
decreased.
BRIEF DESCRIPTION OF THE DRAWINGS
[0018] FIG. 1 is a block diagram illustrating a schematic
configuration of a turbo refrigerator of an embodiment of the
present invention.
[0019] FIG. 2 is a horizontal cross-sectional view illustrating the
turbo compressor of the embodiment of the present invention.
[0020] FIG. 3A is a schematic diagram illustrating a lubricant
supply unit of the embodiment of the present invention.
[0021] FIG. 3B is a schematic diagram illustrating a lubricant
supply unit of the embodiment of the present invention.
[0022] FIG. 3C is a schematic diagram illustrating a lubricant
supply unit of the embodiment of the present invention.
DETAILED DESCRIPTION OF THE INVENTION
[0023] Hereinafter, an example embodiment of the present invention
will be described by referring to FIGS. 1 to 3C. In the
corresponding drawings used for the following description, the
scales of the members are appropriately changed so that the members
have recognizable sizes.
[0024] FIG. 1 is a block diagram illustrating a schematic
configuration of a turbo refrigerator S1 of the embodiment. The
turbo refrigerator S1 of the embodiment is installed at, for
example, a building, a factory, or the like in order to generate
air-conditioning cooling water, and includes a condenser 1, an
economizer 2, an evaporator 3, and a turbo compressor 4.
[0025] A compressed refrigerant gas X1 as a compressed gas
refrigerant is supplied to the condenser 1, and the compressed
refrigerant gas X1 is cooled and liquefied therein so that it
becomes a refrigerant liquid X2. Further, as shown in FIG. 1, the
condenser 1 is connected to the turbo compressor 4 through a
passage R1 where the compressed refrigerant gas X1 flows, and is
connected to the economizer 2 through a passage R2 where the
refrigerant liquid X2 flows. An expansion valve 5 is installed in
the passage R2 so as to depressurize the refrigerant liquid X2.
[0026] The economizer 2 temporarily stores the refrigerant liquid
X2 depressurized at the expansion valve 5. The economizer 2 is
connected to the evaporator 3 through a passage R3 where the
refrigerant liquid X2 flows, and is connected to the turbo
compressor 4 through a passage R4 where a gas phase component X3 of
the refrigerant generated at the economizer 2 flows. An expansion
valve 6 is installed at the passage R3 so as to further
depressurize the refrigerant liquid X2. Further, the passage R4 is
connected to the turbo compressor 4 so as to supply the gas phase
component X3 to a second compression stage 22 described later and
provided in the turbo compressor 4.
[0027] The evaporator 3 cools a cooling object by taking
evaporation heat from the cooling object such as water in a manner
such that the refrigerant liquid X2 evaporates. The evaporator 3 is
connected to the turbo compressor 4 through a passage R5 where a
refrigerant gas X4 generated by the evaporation of the refrigerant
liquid X2 flows. The passage R5 is connected to a first compression
stage 21 described later and provided in the turbo compressor
4.
[0028] The turbo compressor 4 compresses the refrigerant gas X4 so
that it becomes the compressed refrigerant gas X1. As described
above, the turbo compressor 4 is connected to the condenser 1
through the passage R1 where the compressed refrigerant gas X1
flows, and is connected to the evaporator 3 through the passage R5
where the refrigerant gas X4 flows.
[0029] In the turbo refrigerator S1, the compressed refrigerant gas
X1 supplied to the condenser 1 through the passage R1 is cooled and
liquefied by the condenser 1 so that it becomes the refrigerant
liquid X2. The refrigerant liquid X2 is depressurized by the
expansion valve 5 when it is supplied to the economizer 2 through
the passage R2, is temporarily stored in a depressurized state at
the economizer 2. Then, the refrigerant liquid X2 is further
depressurized by the expansion valve 6 when it is supplied to the
evaporator 3 through the passage R3. Accordingly, the depressurized
refrigerant liquid X2 is supplied to the evaporator 3. The
refrigerant liquid X2 supplied to the evaporator 3 is evaporated by
the evaporator 3 so that it becomes the refrigerant gas X4, and is
supplied to the turbo compressor 4 through the passage R5. The
refrigerant gas X4 supplied to the turbo compressor 4 is compressed
by the turbo compressor 4 so that it becomes the compressed
refrigerant gas X1, and is supplied again to the condenser 1
through the passage R1.
[0030] 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 through the passage R4, and is compressed
together with the refrigerant gas X4 so that it is supplied as the
compressed refrigerant gas X1 to the condenser 1 through the
passage R1.
[0031] In the turbo refrigerator S1, the cooling object is cooled
or frozen in a manner such that the refrigerant liquid X2 takes
evaporation heat from the cooling object when evaporating from the
evaporator 3.
[0032] Next, the turbo compressor 4 of the embodiment will be
described in more detail. FIG. 2 is a horizontal cross-sectional
view illustrating the turbo compressor 4 of the embodiment.
[0033] As shown in FIG. 2, the turbo compressor 4 of the embodiment
includes a motor unit 10, a compressor unit 20, and a gear unit
30.
[0034] The motor unit 10 includes a motor 12 which includes an
output shaft 11 and serves as a drive source which drives the
compressor unit 20, and a motor casing 13 which surrounds the motor
12 and in which the motor 12 is installed. The drive source driving
the compressor unit 20 is not limited to the motor 12. For example,
an internal combustion engine may be used. The output shaft 11 of
the motor 12 is rotatably supported by a first bearing 14 and a
second bearing 15 fixed to the motor casing 13.
[0035] The compressor unit 20 includes the first compression stage
21 which suctions and compresses the refrigerant gas X4 (refer to
FIG. 1), and the second compression stage 22 which further
compresses the refrigerant gas X4 compressed at the first
compression stage 21 and discharges it as the compressed
refrigerant gas X1 (refer to FIG. 1).
[0036] The first compression stage 21 includes a first impeller 21a
which discharges the refrigerant gas X4 in the radial direction by
applying kinetic energy to the refrigerant gas X4 supplied in the
thrust direction, a first diffuser 21b which compresses the
refrigerant gas X4 by converting the kinetic energy applied to the
refrigerant gas X4 into potential energy by the first impeller 21a,
a first scroll chamber 21c (a scroll chamber) which guides the
refrigerant gas X4 compressed by the first diffuser 21b to the
outside of the first compression stage 21, and a suction port 21d
which supplies the refrigerant gas X4 to the first impeller 21a by
suctioning the refrigerant gas X4. The first diffuser 21b, the
first scroll chamber 21c, and the suction port 21d are formed by a
first impeller casing 21e surrounding the first impeller 21a.
[0037] The rotation shaft 23 is provided inside the compressor unit
20 so as to extend across the first compression stage 21 and the
second compression stage 22. The first impeller 21a is fixed to the
rotation shaft 23, and the rotation shaft 23 rotates when rotation
power is transmitted from the motor 12 thereto. Further, inlet
guide vanes 21f are provided in the suction port 21d of the first
compression stage 21 so as to adjust the suction amount of the
first compression stage 21. Each inlet guide vane 21f is rotatably
supported by the drive mechanism 21g fixed to the first impeller
casing 21e so that the apparent area in the stream direction of the
refrigerant gas X4 is changeable. Further, a vane drive unit 24 is
installed at the outside of the first impeller casing 21e so that
the vane drive unit is connected to the drive mechanism 21g and
rotationally drives each inlet guide vane 21f.
[0038] The second compression stage 22 includes a second impeller
22a which discharges the refrigerant gas X4 by applying kinetic
energy to the refrigerant gas X4 compressed at the first
compression stage 21 and supplied in the thrust direction, a second
diffuser 22b which compresses and discharges the compressed
refrigerant gas X1 by converting the kinetic energy applied to the
refrigerant gas X4 into potential energy using the second impeller
22a, a second scroll chamber 22c which guides the compressed
refrigerant gas X1 discharged from the second diffuser 22b to the
outside of the second compression stage 22, and an introduction
scroll chamber 22d which guides the refrigerant gas X4 compressed
by 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 surrounding the second impeller 22a.
[0039] The second impeller 22a is fixed to the rotation shaft 23 so
that the rear surface thereof is coupled to the rear surface of the
first impeller 21a, and rotates when rotation power is transmitted
from the motor 12 to the rotation shaft 23. The second scroll
chamber 22c is connected to the passage R1 (refer to FIG. 1)
supplying the compressed refrigerant gas X1 to the condenser 1
(refer to FIG. 1), and supplies the compressed refrigerant gas X1
guided out from the second compression stage 22 to the passage
R1.
[0040] The first scroll chamber 21c of the first compression stage
21 and the introduction scroll chamber 22d of the second
compression stage 22 are connected to each other through an
external pipe (not shown) that is provided separately from the
first compression stage 21 and the second compression stage 22. The
refrigerant gas X4 compressed at the first compression stage 21 is
supplied to the second compression stage 22 through the external
pipe. The passage R4 (refer to FIG. 1) is connected to the external
pipe, and the gas phase component X3 of the refrigerant generated
at the economizer 2 is configured to be supplied to the second
compression stage 22 through the external pipe.
[0041] The rotation shaft 23 is rotatably supported by a third
bearing 26 fixed to the second impeller casing 22e at a space 25
between the first compression stage 21 and the second compression
stage 22 and a fourth bearing 27 fixed to the gear unit 30 of the
second impeller casing 22e.
[0042] The gear unit 30 is used to transmit rotation power of the
motor 12 to the rotation shaft 23, and includes a spur gear 31
which is fixed to the output shaft 11, a pinion gear 32 which is
fixed to the rotation shaft 23 and meshes with the spur gear 31,
and a gear casing 33 which accommodates the spur gear 31 and the
pinion gear 32. Furthermore, the gear unit 30 includes an oil tank
34 which is provided in the gear casing 33 and storing lubricant
therein, a nozzle 35 which spraying and supplying lubricant to a
sliding position sliding with the operation of the motor 12, a
supply pipe 36 which is connected to the nozzle 35, and a lubricant
supply unit 40 (hereinafter, simply referred to as a "supply unit
40") which sends lubricant stored in the oil tank 34 toward the
supply pipe 36 and the nozzle 35. As the above-described sliding
positions, a bearing such as a fourth bearing 27 or a meshing
portion between the spur gear 31 and the pinion gear 32 may be
mentioned.
[0043] The spur gear 31 has an outer diameter larger than that of
the pinion gear 32, and transmits the rotation power of the motor
12 to the rotation shaft 23 so that the rpm of the rotation shaft
23 increases with respect to the rpm of the output shaft 11 by the
corporation between the spur gear 31 and the pinion gear 32. The
transmission method is not limited thereto, and the diameters of
the plurality of gears may be set so that the rpm (number of
rotations) of the rotation shaft 23 is equal to or lower than the
rpm of the output shaft 11.
[0044] The gear casing 33 is molded separately from the motor
casing 13 and the second impeller casing 22e, and connects them
each other. The interior of the gear casing 33 is provided with an
accommodation space 33a that accommodates the spur gear 31, the
pinion gear 32, the nozzle 35, and the supply pipe 36.
[0045] The oil tank 34 is a tank that is used to collect and store
lubricant supplied to the sliding position with the operation of
the motor 12 and lubricating the sliding position. The lubricant
stored in the oil tank 34 may contain minute metal powder or sludge
formed at the sliding position.
[0046] The nozzle 35 sprays and supplies lubricant to the sliding
position of the fourth bearing 27 or the meshing portion between
the spur gear 31 and the pinion gear 32 to lubricate the sliding
position. The supply pipe 36 is a pipe member that is provided
between the nozzle 35 and the supply unit 40 and supplying
lubricant to the nozzle 35. Another nozzle may be provided to
supply lubricant to the sliding position of the first bearing 14 or
the third bearing 26.
[0047] Next, the supply unit 40 which is the characteristic point
of the embodiment will be described in more detail. FIGS. 3A to 3C
are schematic diagrams the supply unit 40 of the 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 blocking valve 43, a second blocking valve 44, and a
control valve 45. The pump 41, the oil filter 42, the first
blocking valve 43, the second blocking valve 44, and the control
valve 45 are all installed at an oil tank cover 46. The oil tank
cover 46 is provided to seal an open portion 34a formed in the oil
tank 34. The oil tank cover 46 is molded by, for example, casting,
and is fixed to the oil tank 34 through fastening bolts 46a. The
second supply pipe 47 is connected to the supply unit 40. The
second supply pipe 47 is a pipe member that is connected to the
supply pipe 36 (refer to FIG. 2).
[0048] The pump 41 is installed at the rear surface of the oil tank
cover 46, and is provided inside the oil tank 34. The pump 41 sends
lubricant stored in the oil tank 34 toward the first pre-filtering
passage 46b formed in the oil tank cover 46. The discharge amount
from the pump 41 is set to be constant. The oil filter 42 is
installed in a filter installation space 46c formed at the front
surface of the oil tank cover 46 so as to be replaceable when
necessary. The oil filter 42 filters the lubricant sent from the
pump 41 and removes minute metal powder or sludge contained in the
lubricant.
[0049] The first blocking valve 43 is provided at the front surface
of the oil tank cover 46. The first blocking valve 43 is connected
to the pump 41 through the first pre-filtering passage 46b.
Further, the first blocking valve 43 is connected to the filter
installation space 46c through the second pre-filtering passage 46d
formed in the oil tank cover 46. Further, the first blocking valve
43 is a valve that blocks the stream of the lubricant flowing
toward the oil filter 42 by interrupting the connection between the
first pre-filtering passage 46b and the second pre-filtering
passage 46d. The first blocking valve 43 is opened or closed by an
operation of a first handle 43a.
[0050] The second blocking valve 44 is provided between the filter
installation space 46c and the second supply pipe 47 at the front
surface side of the oil tank cover 46. The second blocking valve 44
is a valve that blocks the stream of the lubricant flowing toward
the supply pipe 36 by interrupting the connection between the
filter installation space 46c and the second supply pipe 47. The
second blocking valve 44 is opened or closed by an operation of a
second handle 44a.
[0051] The control valve 45 is a valve that adjusts the flow rate
of the lubricant returning to the oil tank 34 by dividing the
stream of the lubricant sent from the pump 41. The control valve 45
is installed at an installation portion 46e formed in the oil tank
cover 46. The surface of the control valve 45 facing the
installation portion 46e is formed in a planar shape. This surface
is provided with an inflow hole and an outflow hole (not shown).
The flow rate of the lubricant flowing from the inflow hole into
the control valve 45 and flowing out from the outflow hole is
adjustable. The flow rate of the lubricant is adjusted by an
operation of a third handle 45a.
[0052] The installation portion 46e is formed in a planar shape. A
gasket (a seal member, not shown in figure) is interposed between
the control valve 45 and the installation portion 46e so as to
liquid-tightly seal therebetween. The gasket is provided with
penetration holes which correspond to the inflow hole and the
outflow hole of the control valve 45. The surface of the control
valve 45 facing the installation portion 46e and the installation
portion 46e are both formed in a planar shape. Accordingly, the
liquid-tightness therebetween may be ensured.
[0053] The oil tank cover 46 is provided with a dividing passage
46f (a first passage) and a returning passage 46g (a second
passage). The dividing passage 46f is divided from the filter
installation space 46c and is opened from the installation portion
46e. That is, the dividing passage 46f is provided to be divided
from the passage between the pump 41 and the oil filter 42. The
open position of the dividing passage 46f in the installation
portion 46e is set to a position facing the inflow hole of the
control valve 45. As described above, since the gasket is
interposed between the control valve 45 and the installation
portion 46e, the dividing passage 46f is liquid-tightly connected
to the inflow hole of the control valve 45. That is, the dividing
passage 46f is directly connected to the filter installation space
46c and the control valve 45. The dividing passage 46f is formed by
extension hole portions which extend in a predetermined direction,
and the predetermined end portion of the extension hole is sealed
by a set screw 46h (a slotted set screw) threaded thereinto.
[0054] The returning passage 46g is provided between the
installation portion 46e and the rear surface of the oil tank cover
46. One end of the returning passage 46g is opened from the
installation portion 46e, and the other end thereof is opened from
the rear surface of the oil tank cover 46 (that is, the interior of
the oil tank 34). The open position of the returning passage 46g in
the installation portion 46e is set to a position facing the
outflow hole of the control valve 45. As described above, since the
gasket is interposed between the control valve 45 and the
installation portion 46e, the returning passage 46g is
liquid-tightly connected to the outflow hole of the control valve
45. That is, the returning passage 46g is directly connected to the
interior of the oil tank 34 by the control valve 45.
[0055] A lubricant supply operation of the supply unit 40 will be
described.
[0056] First, the first blocking valve 43 and the second blocking
valve 44 are opened by the operation of the first handle 43a and
the second handle 44a. By the operation of the pump 41, the
lubricant stored in the oil tank 34 is sent toward the first
pre-filtering passage 46b. The lubricant sent to the first
pre-filtering passage 46b flows into the filter installation space
46c through the first blocking valve 43 and the second
pre-filtering passage 46d. The lubricant is filtered while flowing
into the oil filter 42 provided in the filter installation space
46c. By this filtering, minute metal powder or sludge contained in
the lubricant is removed. The lubricant filtered by the oil filter
42 is sent to the second supply pipe 47 through the second blocking
valve 44. The lubricant sent to the second supply pipe 47 is
supplied to the nozzle 35 through the supply pipe 36, and is
sprayed from the nozzle 35 to the sliding position.
[0057] Part of the lubricant flowing into the filter installation
space 46c flows through the dividing passage 46f and flows into the
control valve 45. The lubricant passing through the control valve
45 and flowing out from the control valve 45 flows through the
returning passage 46g and returns into the oil tank 34 again. By
the operation of the third handle 45a, it is possible to adjust of
the flow rate of the lubricant divided from the filter installation
space 46c, flowing through the dividing passage 46f, the control
valve 45, and the returning passage 46g, and returning into the oil
tank 34. When the flow rate of the lubricant passing through the
control valve 45 and returning to the oil tank 34 increases, the
flow rate of the lubricant passing through the second supply pipe
47 and flowing toward the nozzle 35 decreases. For this reason, it
is possible to adjust the flow rate of the lubricant supplied to
the sliding position of the turbo compressor 4 by operating the
third handle 45a. As described above, the lubricant supply
operation in the supply unit 40 is completed.
[0058] Since the dividing passage 46f and the returning passage 46g
are opened from the installation portion 46e, when the control
valve 45 is provided in the installation portion 46e, the dividing
passage 46f and the returning passage 46g are both directly
connected to the control valve 45. Accordingly, it is possible to
decrease the number of components such as pipes connecting the
control valve 45 to the pump 41 and the oil tank 34. When the
number of components is decreased, it is possible to simplify the
assembly of the supply unit 40 and to suppress oil leakage.
[0059] Further, the lubricant returning into the oil tank 34
through the control valve 45 is the lubricant divided before
passing through the oil filter 42. For this reason, it is possible
to suppress the amount of the lubricant filtered at the oil filter
42 and to extend the durability of the oil filter 42.
[0060] Next, an operation of the turbo compressor 4 of the
embodiment will be described.
[0061] First, rotation power of the motor 12 is transmitted to the
rotation shaft 23 through the spur gear 31 and the pinion gear 32.
Accordingly, the first impeller 21a and the second impeller 22a of
the compressor unit 20 are rotationally driven.
[0062] When the first impeller 21a is rotationally driven, the
suction port 21d of the first compression stage 21 becomes a
negative pressure state, and the refrigerant gas X4 flows from the
passage R5 into the first compression stage 21 through the suction
port 21d. The refrigerant gas X4 flowing into the first compression
stage 21 flows into the first impeller 21a in the thrust direction,
and is discharged in the radial direction while kinetic energy is
applied thereto by the first impeller 21a. The refrigerant gas X4
discharged from the first impeller 21a is compressed by the first
diffuser 21b by converting kinetic energy into potential energy.
The refrigerant gas X4 discharged from the first diffuser 21b is
guided to the outside of the first compression stage 21 through the
first scroll chamber 21c. The refrigerant gas X4 guided to the
outside of the first compression stage 21 is supplied to the second
compression stage 22 through an external pipe (not shown).
[0063] The refrigerant gas X4 supplied to the second compression
stage 22 flows into the second impeller 22a in the thrust direction
through the introduction scroll chamber 22d, and is discharged in
the radial direction while kinetic energy is applied thereto by the
second impeller 22a. The refrigerant gas X4 discharged from the
second impeller 22a is further compressed by converting kinetic
energy into potential energy by the second diffuser 22b, so that it
becomes the compressed refrigerant gas X1. The compressed
refrigerant gas X1 discharged from the second diffuser 22b is
guided the outside of the second compression stage 22 through the
second scroll chamber 22c. The compressed refrigerant gas X1 guided
to the outside of the second compression stage 22 is supplied to
the condenser 1 through the passage R1.
[0064] As described above, the operation of the turbo compressor 4
is completed.
[0065] According to the embodiment, the following advantages may be
obtained.
[0066] According to the embodiment, there is an advantage in that
the number of supply pipes or nozzles supplying the lubricant to
the fourth bearing 27 and the meshing portion 38 may be decreased.
Further, in the turbo compressor 4 and the turbo refrigerator S1
including the turbo compressor, there is an advantage in that
manufacturing effort and cost may be reduced.
[0067] While preferred embodiments of the present invention have
been described and illustrated above, it should be understood that
these are examples of the present invention and are not to be
considered as limiting. Additions, omissions, substitutions, and
other modifications can be made without departing from the spirit
or scope of the present invention. Accordingly, the present
invention is not to be considered as being limited by the foregoing
description, and is only limited by the scope of the appended
claims.
[0068] For example, in the above-described embodiment, the dividing
passage 46f and the returning passage 46g are both opened from the
installation portion 46e, but the present invention is not limited
thereto. For example, any one of them may be opened from the
installation portion 46e. Only by a configuration in which one
passage is opened from the installation portion 46e, the number of
components such as pipes may be decreased.
[0069] Further, in the above-described embodiment, the dividing
passage 46f is divided from the filter installation space 46c, but
the present invention is not limited thereto. For example, the
dividing passage may be divided from the passage through which the
lubricant filtered at the oil filter 42 flows.
[0070] Further, in the above-described embodiment, the installation
portion 46e is formed in a planar shape, but only the gap between
the installation portion 46e and the control valve 45 may be
liquid-tightly sealed. For example, a step portion may be provided
between the dividing passage 46f and the returning passage 46g in
the installation portion 46e.
* * * * *