FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
OIL FEED COMPONENT, COMPRESSOR, AND REFRIGERATION CYCLE DEVICE
MITSUBISHI ELECTRIC CORPORATION, A CORPORATION ORGANISED AND
EXISTING UNDER THE LAWS OF JAPAN, WHOSE ADDRESS IS 7-3,
MARUNOUCHI 2-CHOME, CHIYODA-KU, TOKYO 1008310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE INVENTION
AND THE MANNER IN WHICH IT IS TO BE PERFORMED.
2
DESCRIPTION
Technical Field
[0001]
The present disclosure relates to an oil feed component provided in a5
compressor to improve the capacity to supply refrigerating machine oil to sliding parts
in a low-rotation speed range, and also relates to a compressor including the oil feed
component, and a refrigeration cycle device including the compressor.
Background Art
[0002]10
In a conventional compressor, an oil feed hole is formed in a rotation shaft of
the compressor and opened at one end portion of the rotation shaft. When the
rotation shaft rotates, refrigerating machine oil serving as lubrication oil is suctioned
into the oil feed hole. The refrigerating machine oil suctioned into the oil feed hole is
supplied to sliding parts of a compression mechanism and other machines. Another15
conventional compressor has also been proposed, in which an oil feed component is
provided at an end portion of a rotation shaft at which an oil feed hole is opened, and
is designed to improve the capacity to supply refrigerating machine oil to sliding parts
in a state in which the rotation shaft falls within a low-rotation speed range (see
Patent Literature 1).20
[0003]
Specifically, Patent Literature 1 discloses the oil feed component which is
referred to as "suction part." The oil feed component described in Patent Literature
1 includes a main plate portion shaped like a flat plate. A through hole is formed on
the main plate portion. The main plate portion is provided with a plurality of25
engagement claws, each of which protrudes from the main plate portion at a position
near its outer circumferential portion relative to the through hole. The plurality of
engagement claws are inserted into the oil feed hole in the rotation shaft, and the
outer surfaces of the plurality of engagement claws come into contact with an inner
circumferential surface of the rotation shaft, so that the oil feed component described30
3
in Patent Literature 1 is fixed to the end portion of the rotation shaft at which the oil
feed hole is opened. In the oil feed component having the configuration as
described above, the through hole is formed on the inner circumferential side relative
to the plurality of engagement claws to be inserted into the oil feed hole. Due to this
structure, the through hole has a diameter smaller than the diameter of the oil feed5
hole in the rotation shaft. As described above, the oil feed component has such a
configuration as to suction refrigerating machine oil into the oil feed hole in the
rotation shaft from the through hole with a diameter smaller than the diameter of the
oil feed hole in the rotation shaft. The oil feed component can thus improve the
capacity to supply refrigerating machine oil to the sliding parts in a state in which the10
rotation shaft falls within a low-rotation speed range.
Citation List
Patent Literature
[0004]
Patent Literature 1: Japanese Utility Model Laid-Open No. S63-15478715
Summary of Invention
Technical Problem
[0005]
In the oil feed component described in Patent Literature 1, each of the
engagement claws extends straightly in the axial direction of the rotation shaft, in20
other words, in a direction in which the oil feed hole is formed. Due to this structure,
in the oil feed component described in Patent Literature 1, at the time of fixing the oil
feed component to the rotation shaft, the engagement claws are inserted into the oil
feed hole in the rotation shaft, while the major portion of the outer surface of each of
the engagement claws is in contact with the inner circumferential surface of the25
rotation shaft. This leads to a problem that it is difficult to attach the oil feed
component described in Patent Literature 1 into the rotation shaft of the compressor
due to an increase in resistance caused by inserting the engagement claws into the
oil feed hole in the rotation shaft.
[0006]30
4
The present disclosure has been made to solve the above problems, and it is a
first object of the present disclosure to provide an oil feed component that is attached
into a rotation shaft of a compressor more easily than a conventional oil feed
component. It is a second object of the present disclosure to provide a compressor
including the oil feed component as described above. It is a third object of the5
present disclosure to provide a refrigeration cycle device including the compressor as
described above.
Solution to Problem
[0007]
An oil feed component according to one embodiment of the present disclosure10
is an oil feed component provided in a compressor including a rotation shaft in which
an oil feed hole is formed to supply refrigerating machine oil suctioned into the oil
feed hole to a compression mechanism, the oil feed hole being opened at a first end
portion, the first end portion being one end portion of the rotation shaft, the oil feed
component including: a main plate portion on which a through hole is formed; and a15
plurality of insertion portions, each of which protrudes from the main plate portion at a
position near an outer circumferential portion of the main plate portion relative to the
through hole, the plurality of insertion portions being inserted into the oil feed hole,
wherein each of the insertion portions includes a base end portion connected to the
main plate portion at a second end portion, the second end portion being one end20
portion of the base end portion, and a tip end portion connected to a third end portion
at a fourth end portion, the third end portion being an other end portion of the base
end portion, the fourth end portion being one end portion of the tip end portion, the tip
end portion having a fifth end portion, the fifth end portion being an other end portion
of the tip end portion, the fifth end portion being a tip end of the insertion portion,25
where an imaginary straight line passing through the through hole and perpendicular
to the main plate portion is defined as a first imaginary straight line, in each of the
base end portions, the third end portion is located at a position furthest from the first
imaginary straight line, and in each of the tip end portions, the fourth end portion is
located at a position furthest from the first imaginary straight line, and in each of the30
5
insertion portions, a connection portion is in contact with an inner circumferential
surface of the rotation shaft, and thereby the oil feed component is fixed to the
rotation shaft, the connection portion being a location where the third end portion of
the base end portion, and the fourth end portion of the tip end portion are connected.
[0008]5
A compressor according to another embodiment of the present disclosure
includes: a rotating electric machine; a rotation shaft connected to the rotating electric
machine to rotate using power of the rotating electric machine; a compression
mechanism connected to the rotation shaft, and configured to compress refrigerant
suctioned from an exterior by using power of the rotating electric machine transmitted10
through the rotation shaft; a compressor outer shell inside which refrigerating
machine oil is retained, the compressor outer shell having the rotating electric
machine, the rotation shaft, and the compression mechanism accommodated therein;
and the oil feed component according to one embodiment of the present disclosure,
wherein in the rotation shaft, an oil feed hole is formed and opened at one end portion15
of the rotation shaft to supply the refrigerating machine oil suctioned into the oil feed
hole to the compression mechanism, and each of the insertion portions of the oil feed
component is inserted into the oil feed hole, the connection portion of each of the
insertion portions is in contact with the inner circumferential surface of the rotation
shaft, and thereby the oil feed component is fixed to the rotation shaft.20
[0009]
A refrigeration cycle device according to still another embodiment of the
present disclosure includes: the compressor according to another embodiment of the
present disclosure; a radiator through which refrigerant compressed by the
compressor transfers heat; a pressure-reducing device configured to reduce a25
pressure of the refrigerant flowing out from the radiator; and an evaporator through
which the refrigerant flowing out from the pressure-reducing device evaporates.
Advantageous Effects of Invention
[0010]
6
In the oil feed component according to one embodiment of the present
disclosure, at the time of fixing this oil feed component to the rotation shaft, each of
the insertion portions is inserted into the oil feed hole in the rotation shaft, while the
outer surface of the connection portion of each of the insertion portions is in contact
with the inner circumferential surface of the rotation shaft. With this configuration,5
the oil feed component according to one embodiment of the present disclosure can
decrease a resistance caused by inserting each of the insertion portions into the oil
feed hole in the rotation shaft, compared to the conventional oil feed component.
Therefore, it is easier to attach the oil feed component according to one embodiment
of the present disclosure into the rotation shaft of the compressor than the10
conventional oil feed component.
Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 is a vertical cross-sectional view illustrating the overall configuration of a
compressor according to Embodiment 1.15
[Fig. 2] Fig. 2 illustrates a refrigeration cycle device according to Embodiment 1.
[Fig. 3] Fig. 3 is a vertical cross-sectional view illustrating an oil feed component
according to Embodiment 1 attached to an end portion of a rotation shaft of the
compressor.
[Fig. 4] Fig. 4 is a vertical cross-sectional view illustrating the oil feed component20
according to Embodiment 1.
[Fig. 5] Fig. 5 is a plan view illustrating the oil feed component according to
Embodiment 1.
[Fig. 6] Fig. 6 is a schematic diagram illustrating the oil feed component according to
Embodiment 1 when viewed from the side.25
[Fig. 7] Fig. 7 is a schematic diagram illustrating an oil feed component according to
Comparative Example when viewed from the side.
[Fig. 8] Fig. 8 is a schematic diagram illustrating an oil feed component according to
Comparative Example when viewed from the side.
7
[Fig. 9] Fig. 9 is a vertical cross-sectional view illustrating the oil feed component
according to Embodiment 2.
[Fig. 10] Fig. 10 is a bottom view illustrating the oil feed component according to
Embodiment 2.
Description of Embodiments5
[0012]
Embodiment 1
Fig. 1 is a vertical cross-sectional view illustrating the overall configuration of a
compressor according to Embodiment 1.
[Configuration of compressor 1]10
As illustrated in Fig. 1, a compressor 1 according to Embodiment 1 that is a
rolling piston compressor is shown as an example of the compressor according to the
present disclosure. The compressor 1 includes a compressor outer shell 10, a first
suction pipe 2A, a second suction pipe 2B, a suction muffler 3, a compression
mechanism 20, a rotating electric machine 30, a rotation shaft 40, and a discharge15
pipe 4. The compressor outer shell 10 constitutes the outer shell of the compressor
1. Through the first suction pipe 2A and the second suction pipe 2B, refrigerant is
supplied to the interior of the compressor outer shell 10. The suction muffler 3 is
connected to the first suction pipe 2A and the second suction pipe 2B. The
compression mechanism 20 is connected to the first suction pipe 2A and the second20
suction pipe 2B, and configured to compress refrigerant. The rotating electric
machine 30 includes a rotor 31 and a stator 32. The rotation shaft 40 is connected
to the rotor 31 of the rotating electric machine 30 to rotate with the rotor 31. Through
the discharge pipe 4, refrigerant compressed in the compression mechanism 20 is
discharged to the outside of the compressor outer shell 10.25
The configuration of the compressor 1 is described below in detail.
[0013]
(Compressor outer shell 10)
The compressor outer shell 10 constitutes the outer shell of the compressor 1,
and has the compression mechanism 20, the rotating electric machine 30, the rotation30
8
shaft 40, and other elements accommodated therein. The compressor outer shell 10
includes a head portion 11, a bottom portion 13, and a body portion 12. The head
portion 11 constitutes the outer shell of an upper part of the compressor 1. The
bottom portion 13 constitutes the outer shell of a lower part of the compressor 1.
The body portion 12 constitutes the outer shell of a middle part of the compressor 1.5
The head portion 11 is attached to the top of the body portion 12, while the bottom
portion 13 is attached to the bottom of the body portion 12.
[0014]
The head portion 11 that constitutes the upper part of the compressor outer
shell 10 is, for example, substantially bowl-shaped as illustrated in Fig. 1. The10
discharge pipe 4 is connected to the head portion 11 through which the interior of the
compressor outer shell 10 communicates with the exterior of the compressor outer
shell 10.
[0015]
The body portion 12 constitutes the middle part of the compressor outer shell15
10 and is, for example, substantially cylindrical as illustrated in Fig. 1. The first
suction pipe 2A and the second suction pipe 2B through which refrigerant is supplied
to the interior of the compressor outer shell 10 are connected to the body portion 12.
The stator 32 of the rotating electric machine 30 is installed on the inner
circumferential surface of the body portion 12. The compression mechanism 20 is20
installed on the inner circumferential surface of the body portion 12. In the present
Embodiment 1, a rolling piston compression mechanism is employed as the
compression mechanism 20. In this case, the compression mechanism 20 is
installed on the inner circumferential surface of the body portion 12 often on the lower
side of the position where the stator 32 is installed.25
[0016]
The bottom portion 13 constitutes the lower part of the compressor outer shell
10 and is, for example, substantially bowl-shaped as illustrated in Fig. 1. In the
bottom portion 13, refrigerating machine oil 6 serving as lubrication oil is retained.
That is, the refrigerating machine oil 6 is retained in the compressor outer shell 10.30
9
The refrigerating machine oil 6 is supplied to the compression mechanism 20 and
other machines to reduce a friction between sliding parts of the compression
mechanism 20 and other machines.
[0017]
(First suction pipe 2A and second suction pipe 2B)5
As described above, the first suction pipe 2A and the second suction pipe 2B
are connected to the body portion 12 of the compressor outer shell 10. One end
portion of the first suction pipe 2A communicates with a first cylinder 21A of the
compression mechanism 20. The first cylinder 21A will be described later. The
other end portion of the first suction pipe 2A communicates with the suction muffler 3.10
One end portion of the second suction pipe 2B communicates with a second cylinder
21B of the compression mechanism 20. The second cylinder 21B will be described
later. The other end portion of the second suction pipe 2B communicates with the
suction muffler 3.
[0018]15
(Suction muffler 3)
The suction muffler 3 serves as a muffler configured to reduce refrigerant
sound and other sound generated when refrigerant flows into the compressor 1. The
suction muffler 3 also serves as an accumulator capable of retaining liquid refrigerant
therein. The suction muffler 3 communicates with the first suction pipe 2A and the20
second suction pipe 2B as described above.
[0019]
(Compression mechanism 20)
The compression mechanism 20 is connected to the rotation shaft 40 and
configured to compress refrigerant suctioned from the exterior by using power of the25
rotating electric machine 30 transmitted through the rotation shaft 40. In the present
Embodiment 1, refrigerant flowing into the suction muffler 3 is supplied through the
first suction pipe 2A and the second suction pipe 2B to the compression mechanism
20. That is, the compression mechanism 20 suctions refrigerant from the exterior
through the first suction pipe 2A and the second suction pipe 2B, and compresses this30
10
refrigerant. The refrigerant compressed in the compression mechanism 20 is
emitted to the interior of the compressor outer shell 10. As described above, in the
present Embodiment 1, the rolling piston compression mechanism is employed as the
compression mechanism 20. Accordingly, the compression mechanism 20 includes
a cylinder configured to compress the refrigerant suctioned from the exterior. In the5
present Embodiment 1, the compression mechanism 20 includes, as the cylinder, the
first cylinder 21A and the second cylinder 21B. The first cylinder 21A communicates
with the first suction pipe 2A, and is configured to compress refrigerant supplied from
the first suction pipe 2A. The second cylinder 21B communicates with the second
suction pipe 2B, and is configured to compress refrigerant supplied from the second10
suction pipe 2B.
[0020]
The first cylinder 21A is provided with a first piston 22A that rotates slidably
within the first cylinder 21A. The first piston 22A is connected to the rotation shaft 40
to be capable of performing rotational motion within the first cylinder 21A eccentrically15
to the rotation center of the rotation shaft 40. The rotational motion eccentric to the
rotation center of the rotation shaft 40 is hereinafter referred to as "eccentric rotational
motion." The second cylinder 21B is provided with a second piston 22B that rotates
slidably within the second cylinder 21B. The second piston 22B is connected to the
rotation shaft 40 to be capable of performing the eccentric rotational motion within the20
second cylinder 21B.
[0021]
The first piston 22A is connected to the rotation shaft 40 to be capable of
rotating within the first cylinder 21A with a 180-degree phase shift from the rotation
phase of the second piston 22B rotating within the second cylinder 21B. In other25
words, the second piston 22B is connected to the rotation shaft 40 to be capable of
rotating within the second cylinder 21B with a -180-degree phase shift from the
rotation phase of the first piston 22A rotating within the first cylinder 21A.
[0022]
11
On the upper side of the first cylinder 21A, an upper bearing 24A is provided to
support the rotation shaft 40 in a rotatable manner. The upper bearing 24A closes
an upper-side opening of the first cylinder 21A. A partition plate 25 is provided on
the lower side of the first cylinder 21A. The partition plate 25 closes a lower-side
opening of the first cylinder 21A, while closing an upper-side opening of the second5
cylinder 21B. That is, the partition plate 25 partitions off into a space formed by the
first cylinder 21A and the first piston 22A, and a space formed by the second cylinder
21B and the second piston 22B. In contrast, on the lower side of the second cylinder
21B, a lower bearing 24B is provided to support the rotation shaft 40 in a rotatable
manner. The lower bearing 24B closes a lower-side opening of the second cylinder10
21B.
[0023]
Note that on the upper bearing 24A, a valve (not illustrated) is provided,
through which refrigerant compressed by the first cylinder 21A and the first piston 22A
is emitted. This valve is opened, which allows the space formed by the first cylinder15
21A and the first piston 22A to communicate with a first muffler 23A which will be
described later. On the lower bearing 24B, a valve (not illustrated) is provided,
through which refrigerant compressed by the second cylinder 21B and the second
piston 22B is emitted. This valve is opened, which allows the space formed by the
second cylinder 21B and the second piston 22B to communicate with a second20
muffler 23B which will be described later.
[0024]
On the upper bearing 24A, the first muffler 23A is provided, to which refrigerant
compressed by the first cylinder 21A and the first piston 22A is discharged. Note
that the first muffler 23A is provided with a refrigerant discharge portion (not25
illustrated). With this structure, the refrigerant compressed by the first cylinder 21A
and the first piston 22A is discharged to the first muffler 23A and thereafter emitted to
the interior of the compressor outer shell 10 from the refrigerant discharge portion.
On the lower bearing 24B, the second muffler 23B is provided, to which refrigerant
compressed by the second cylinder 21B and the second piston 22B is discharged.30
12
Note that the second muffler 23B communicates with the first muffler 23A through a
refrigerant flow passage (not illustrated). With this structure, the refrigerant
compressed by the second cylinder 21B and the second piston 22B is discharged to
the second muffler 23B and thereafter flows into the first muffler 23A through the
refrigerant flow passage (not illustrated). The refrigerant flowing into the first muffler5
23A is then emitted from the refrigerant discharge portion of the first muffler 23A to the
interior of the compressor outer shell 10.
[0025]
(Rotating electric machine 30 and rotation shaft 40)
The rotating electric machine 30 includes the rotor 31 configured to transmit its10
own rotations to the rotation shaft 40, and the stator 32 made up of multi-phase
windings wound on a laminated core.
[0026]
The rotation shaft 40 is connected to the rotating electric machine 30, and
rotates using power of the rotating electric machine 30. Through the rotation shaft15
40, the power of the rotating electric machine 30 is transmitted to the compression
mechanism 20. In the present Embodiment 1, the rotation shaft 40 is connected on
its upper end side to the rotor 31 of the rotating electric machine 30. This allows the
rotation shaft 40 to rotate as the rotor 31 rotates. Note that the rotation shaft 40
illustrated in Fig. 1 rotates about an axis extending in an up-down direction of the20
drawing of Fig. 1. The rotation shaft 40 is connected on its lower end side to the
compression mechanism 20. More specifically, the rotation shaft 40 is supported on
its lower end side in a rotatable manner by the upper bearing 24A and the lower
bearing 24B of the compression mechanism 20. Between a location where the
rotation shaft 40 is supported by the upper bearing 24A in a rotatable manner, and a25
location where the rotation shaft 40 is supported by the lower bearing 24B in a
rotatable manner, the first piston 22A and the second piston 22B are connected to the
rotation shaft 40 to be capable of performing the eccentric rotational motion. With
this structure, the rotation shaft 40 rotates as the rotor 31 rotates, while the first piston
22A and the second piston 22B perform the eccentric rotational motion. Refrigerant30
13
is compressed by the first cylinder 21A and the first piston 22A, while refrigerant is
compressed by the second cylinder 21B and the second piston 22B. That is, the
compression mechanism 20 compresses refrigerant suctioned from the exterior, using
power of the rotating electric machine 30 transmitted through the rotation shaft 40.
[0027]5
(Discharge pipe 4)
Through the discharge pipe 4, refrigerant compressed in the compression
mechanism 20 is discharged to the outside of the compressor outer shell 10. That
is, through the discharge pipe 4, high-temperature high-pressure refrigerant in the
compressor outer shell 10 is discharged to the outside of the compressor outer shell10
10.
[0028]
(Centrifugal pump 45)
In the rotation shaft 40, an oil feed hole 42 is formed and opened at an end
portion 41 that is one end portion of the rotation shaft 40. The end portion 41 is15
equivalent to a first end portion. In the present Embodiment 1, the end portion 41 is
a lower end portion of the rotation shaft 40. The oil feed hole 42 extends along the
rotation center of the rotation shaft 40. Further, in the rotation shaft 40, a first oil
feed port 43 and a second oil feed port 44 are formed. The first oil feed port 43 and
the second oil feed port 44 serve as a flow passage through which the refrigerating20
machine oil 6 suctioned into the oil feed hole 42 is supplied to the sliding parts of the
compression mechanism 20. One end portion of the first oil feed port 43, and one
end portion of the second oil feed port 44 communicate with the oil feed hole 42.
The other end portion of the first oil feed port 43, and the other end portion of the
second oil feed port 44 are opened on the outer circumferential surface of the rotation25
shaft 40 at a location facing the compression mechanism 20. Note that in the
present Embodiment 1, the other end portion of the first oil feed port 43 is opened at a
location facing the upper bearing 24A of the compression mechanism 20. The other
end portion of the second oil feed port 44 is opened at a location facing the lower
bearing 24B of the compression mechanism 20.30
14
[0029]
A centrifugal pump 45 is provided within the oil feed hole 42 in the rotation shaft
40. The centrifugal pump 45 is formed by twisting a plate-like part. The centrifugal
pump 45 is a fluid machine configured to pump up the refrigerating machine oil 6,
retained in the bottom portion 13 of the compressor outer shell 10 to serve as5
lubrication oil, by using a centrifugal force generated by rotational motion of the
rotation shaft 40. The refrigerating machine oil 6 pumped up into the oil feed hole 42
by the centrifugal pump 45 is supplied to the sliding parts of the compression
mechanism 20. Specifically, part of the refrigerating machine oil 6 pumped up into
the oil feed hole 42 passes through the first oil feed port 43 and is supplied to the10
sliding parts between the upper bearing 24A of the compression mechanism 20 and
the rotation shaft 40. In addition, part of the refrigerating machine oil 6 pumped up
into the oil feed hole 42 passes through the second oil feed port 44 and is supplied to
the sliding parts between the lower bearing 24B of the compression mechanism 20
and the rotation shaft 40. Examples of the refrigerating machine oil 6 to be used15
include mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl
ether-based, and polyol ester-based lubrication oils.
[0030]
[Operation of rotating electric machine 30]
An electric current is supplied from a power supply (not illustrated) to the20
windings provided on the laminated core of the stator 32 to form a rotating magnetic
field in the stator 32. This causes the rotating magnetic field in the stator 32 to act
on permanent magnets provided in the rotor 31, so that the rotor 31 rotates. The
rotations of the rotor 31 are transmitted through the rotation shaft 40 to the first piston
22A and the second piston 22B to cause the first piston 22A and the second piston25
22B to perform the eccentric rotational motion.
[0031]
[Refrigerant flow]
As the first piston 22A and the second piston 22B perform the eccentric
rotational motion, refrigerant is drawn into the compressor 1. Specifically, as the first30
15
piston 22A and the second piston 22B perform the eccentric rotational motion, low-
pressure refrigerant outside the compressor 1 flows into the suction muffler 3. Low-
pressure refrigerant in gas form, included in the low-pressure refrigerant flowing into
the suction muffler 3, flows into the compression mechanism 20 in the compressor 1
through the first suction pipe 2A and the second suction pipe 2B. Part of the5
refrigerant in gas form having flowed into the compression mechanism 20 is
compressed by the first cylinder 21A and the first piston 22A into high-temperature
high-pressure refrigerant in gas form. This high-temperature high-pressure
refrigerant in gas form flows into the first muffler 23A through the valve on the upper
bearing 24A. The high-temperature high-pressure refrigerant in gas form, having10
flowed into the first muffler 23A, is emitted from the refrigerant discharge portion (not
illustrated) provided on the first muffler 23A to a space in the compressor outer shell
10. The high-temperature high-pressure refrigerant in gas form, having been
emitted to the space in the compressor outer shell 10, then moves to the upper part of
the space in the compressor outer shell 10 through a gap and the like of the rotating15
electric machine 30, and is discharged through the discharge pipe 4.
[0032]
The remaining refrigerant in gas form, having flowed into the compression
mechanism 20, is compressed by the second cylinder 21B and the second piston 22B
into high-temperature high-pressure refrigerant in gas form. This high-temperature20
high-pressure refrigerant in gas form flows into the second muffler 23B through the
valve on the lower bearing 24B. The high-temperature high-pressure refrigerant in
gas form, having flowed into the second muffler 23B, is delivered from the second
muffler 23B through the refrigerant flow passage (not illustrated) to the first muffler
23A. The high-temperature high-pressure refrigerant in gas form, having been25
delivered to the first muffler 23A, is emitted from the refrigerant discharge portion (not
illustrated) provided on the first muffler 23A to the space in the compressor outer shell
10. The high-temperature high-pressure refrigerant in gas form, having been
emitted to the space in the compressor outer shell 10, then moves to the upper part of
16
the space in the compressor outer shell 10 through a gap and the like of the rotating
electric machine 30, and is discharged through the discharge pipe 4.
[0033]
The refrigerating machine oil 6 retained in the bottom portion 13 of the
compressor outer shell 10 is pumped up from the lower end portion of the oil feed5
hole 42 by the centrifugal pump 45 rotating with the rotation shaft 40. The
refrigerating machine oil 6, pumped up from the lower end portion of the oil feed hole
42 to serve as lubrication oil, flows into a gap between the upper bearing 24A and the
rotation shaft 40 through the first oil feed port 43. The refrigerating machine oil 6
also flows into a gap between the lower bearing 24B and the rotation shaft 40 through10
the second oil feed port 44. The refrigerating machine oil 6 flows into these gaps,
which can help smoothly transmit a rotational driving force to the first piston 22A and
the second piston 22B through the rotation shaft 40.
[0034]
Part of the refrigerating machine oil 6 having flowed into the gap between the15
upper bearing 24A and the rotation shaft 40 through the first oil feed port 43 flows into
a gap between the upper bearing 24A and an upper face of the first piston 22A. In
addition, part of the refrigerating machine oil 6 having flowed into the gap between the
lower bearing 24B and the rotation shaft 40 through the second oil feed port 44 flows
into a gap between the lower bearing 24B and a lower face of the second piston 22B.20
The refrigerating machine oil 6 is used to help the first piston 22A and the second
piston 22B to smoothly rotate. However, part of the refrigerating machine oil 6 is
compressed along with the low-pressure refrigerant in gas form, and is thus contained
in high-temperature high-pressure refrigerant in gas form and then discharged.
[0035]25
[Configuration and operation of refrigeration cycle device 200]
Fig. 2 illustrates a refrigeration cycle device according to Embodiment 1.
A refrigeration cycle device 200 includes the compressor 1 according to the
present Embodiment 1, a radiator through which refrigerant compressed by the
compressor 1 transfers heat, a pressure-reducing device 203, such as an electric30
17
expansion valve, configured to reduce a pressure of refrigerant flowing out from the
radiator, and an evaporator through which refrigerant flowing out from the pressure-
reducing device 203 evaporates.
[0036]
The refrigeration cycle device 200 is used for various applications such as a5
hot-water supply device and a refrigeration device. Fig. 2 illustrates an example in
which the refrigeration cycle device 200 is used as an air-conditioning apparatus.
Accordingly, the refrigeration cycle device 200 illustrated in Fig. 2 includes an indoor
side heat exchanger 204 serving as the radiator during heating mode, and an outdoor
side heat exchanger 202 serving as the evaporator during heating mode. The10
refrigeration cycle device 200 illustrated in Fig. 2 is also capable of running in cooling
mode. Accordingly, the refrigeration cycle device 200 includes a four-way switching
valve 201. The four-way switching valve 201 is configured to switch each heat
exchanger between being connected to the discharge pipe 4 that is a refrigerant
discharge port of the compressor 1, and being connected to the suction muffler 3 that15
is a refrigerant suction port of the compressor 1. During cooling mode, the indoor
side heat exchanger 204 serves as the evaporator, while the outdoor side heat
exchanger 202 serves as the radiator.
[0037]
When the refrigeration cycle device 200 is used as an air-conditioning20
apparatus, the indoor side heat exchanger 204 is installed in, for example, an indoor
device. The four-way switching valve 201, the outdoor side heat exchanger 202,
and the pressure-reducing device 203 are installed in, for example, an outdoor
device. Examples of refrigerant to be used in the refrigeration cycle device 200
include an R407C refrigerant, a R410A refrigerant, and a R32 refrigerant.25
Operation of the refrigeration cycle device 200 during heating mode and
cooling mode is described below.
[0038]
When the refrigeration cycle device 200 runs in heating mode, the four-way
switching valve 201 switches the flow passage to a flow passage illustrated by the30
18
solid lines in Fig. 2. With this switching operation, the discharge pipe 4 of the
compressor 1 is connected to the indoor side heat exchanger 204, while the suction
muffler 3 of the compressor 1 is connected to the outdoor side heat exchanger 202.
That is, this brings the indoor side heat exchanger 204 and the outdoor side heat
exchanger 202 into a state in which the indoor side heat exchanger 204 and the5
outdoor side heat exchanger 202 serve as the radiator and the evaporator,
respectively. In this state, high-temperature high-pressure refrigerant in gas form
compressed by the compressor 1 is discharged from this compressor 1, and then the
high-temperature high-pressure refrigerant in gas form flows into the indoor side heat
exchanger 204. The high-temperature high-pressure refrigerant in gas form, having10
flowed into the indoor side heat exchanger 204, condenses, while transferring heat to
room air, into high-pressure refrigerant in liquid form to flow out from the indoor side
heat exchanger 204. At this time, the room air is heated. Note that there are some
types of refrigerants, including a carbon dioxide refrigerant, that do not condense
when transferring heat. In a case of using a refrigerant that condenses when15
transferring heat, the radiator may be referred to as a condenser.
[0039]
The high-pressure refrigerant in liquid form, having flowed out from the indoor
side heat exchanger 204, flows into the pressure-reducing device 203. The high-
pressure refrigerant in liquid form, having flowed into the pressure-reducing device20
203, is reduced in pressure by the pressure-reducing device 203 into low-temperature
low-pressure two-phase gas-liquid refrigerant to flow out from the pressure-reducing
device 203. The low-temperature low-pressure two-phase gas-liquid refrigerant,
having flowed out from the pressure-reducing device 203, flows into the outdoor side
heat exchanger 202. The low-temperature low-pressure two-phase gas-liquid25
refrigerant, having flowed into the outdoor side heat exchanger 202, receives heat
from outside air and evaporates, and then flows out from the outdoor side heat
exchanger 202 as low-pressure refrigerant in gas form or two-phase gas-liquid
refrigerant. The low-pressure refrigerant in gas form or two-phase gas-liquid
refrigerant, having flowed out from the outdoor side heat exchanger 202, is suctioned30
19
into the suction muffler 3 of the compressor 1. The low-pressure refrigerant in gas
form, included in the refrigerant suctioned into the suction muffler 3 of the compressor
1, is compressed by the compression mechanism 20 in the compressor 1 into high-
temperature high-pressure refrigerant in gas form. The high-temperature high-
pressure refrigerant in gas form is discharged from the compressor 1 again. That is,5
the refrigerant circulates as illustrated by the solid arrows in Fig. 2 when the
refrigeration cycle device 200 runs in heating mode.
[0040]
When the refrigeration cycle device 200 runs in cooling mode, the four-way
switching valve 201 switches the flow passage to a flow passage illustrated by the10
dotted lines in Fig. 2. With this switching operation, the discharge pipe 4 of the
compressor 1 is connected to the outdoor side heat exchanger 202, while the suction
muffler 3 of the compressor 1 is connected to the indoor side heat exchanger 204.
That is, this brings the outdoor side heat exchanger 202 and the indoor side heat
exchanger 204 into a state in which the outdoor side heat exchanger 202 and the15
indoor side heat exchanger 204 serve as the radiator and the evaporator,
respectively. In this state, high-temperature high-pressure refrigerant in gas form
compressed by the compressor 1 is discharged from this compressor 1, and then the
high-temperature high-pressure refrigerant in gas form flows into the outdoor side
heat exchanger 202. The high-temperature high-pressure refrigerant in gas form,20
having flowed into the outdoor side heat exchanger 202, condenses, while
transferring heat to outside air, into high-pressure refrigerant in liquid form to flow out
from the outdoor side heat exchanger 202.
[0041]
The high-pressure refrigerant in liquid form, having flowed out from the outdoor25
side heat exchanger 202, flows into the pressure-reducing device 203. The high-
pressure refrigerant in liquid form, having flowed into the pressure-reducing device
203, is reduced in pressure by the pressure-reducing device 203 into low-temperature
low-pressure two-phase gas-liquid refrigerant to flow out from the pressure-reducing
device 203. The low-temperature low-pressure two-phase gas-liquid refrigerant,30
20
having flowed out from the pressure-reducing device 203, flows into the indoor side
heat exchanger 204. The low-temperature low-pressure two-phase gas-liquid
refrigerant, having flowed into the indoor side heat exchanger 204, receives heat from
room air and evaporates, and then flows out from the indoor side heat exchanger 204
as low-pressure refrigerant in gas form or two-phase gas-liquid refrigerant. At this5
time, the room air is cooled. The low-pressure refrigerant in gas form or two-phase
gas-liquid refrigerant, having flowed out from the indoor side heat exchanger 204, is
suctioned into the suction muffler 3 of the compressor 1. The low-pressure
refrigerant in gas form, included in the refrigerant suctioned into the suction muffler 3
of the compressor 1, is compressed by the compression mechanism 20 in the10
compressor 1 into high-temperature high-pressure refrigerant in gas form. The high-
temperature high-pressure refrigerant in gas form is discharged from the compressor
1 again. That is, the refrigerant circulates as illustrated by the dotted arrows in Fig. 2
when the refrigeration cycle device 200 runs in cooling mode.
[0042]15
(Oil feed component 100)
In the compressor 1 according to the present Embodiment 1, the oil feed
component 100 is attached to the end portion 41 of the rotation shaft 40 to improve
the capacity to supply the refrigerating machine oil 6 to the sliding parts of the
compression mechanism 20 in a state in which the rotation shaft 40 falls within a low-20
rotation speed range. The oil feed component 100 according to the present
Embodiment 1 is described below in detail.
[0043]
Fig. 3 is a vertical cross-sectional view illustrating the oil feed component
according to Embodiment 1 attached to the end portion of the rotation shaft of the25
compressor. Fig. 4 is a vertical cross-sectional view illustrating the oil feed
component according to Embodiment 1. Fig. 5 is a plan view illustrating the oil feed
component according to Embodiment 1.
The oil feed component 100 is made of, for example, a plate-like part of metal.
In the present Embodiment 1, a plate-like part of spring steel GB-65Mn is used to30
21
make the oil supply component 100. Note that material of the oil feed component
100 is not particularly limited, and other plate-like parts of metal such as SPCC,
SUS304, or S50C may be used to make the oil feed component 100.
[0044]
As illustrated in Figs. 3 to 5, the oil feed component 100 includes a main plate5
portion 110, and a plurality of insertion portions 120. For example, the main plate
portion 110 is shaped like a flat plate. On the main plate portion, a through hole 111
is formed at, for example, a substantially center position. Each of the insertion
portions 120 protrudes from the main plate portion 110 at a position near an outer
circumferential portion 112 of the main plate portion 110 relative to the through hole10
111. Each of the insertion portions 120 is inserted into the oil feed hole 42 in the
rotation shaft 40. To be more specific, the plurality of insertion portions 120 are
inserted into the oil feed hole 42 in the rotation shaft 40, and the outer surfaces of the
plurality of insertion portions 120 are in contact with an inner circumferential surface
46 of the rotation shaft 40, so that the oil feed component 100 is fixed to the end15
portion 41 of the rotation shaft 40.
[0045]
In the oil feed component 100 having the configuration as described above, the
through hole 111 is formed on the inner circumferential side relative to the plurality of
insertion portions 120 to be inserted into the oil feed hole 42. In view of that, the20
through hole 111 has a diameter smaller than the diameter of the oil feed hole 42 in
the rotation shaft 40. As described above, the oil feed component 100 has such a
configuration as to suction the refrigerating machine oil 6 into the oil feed hole 42 in
the rotation shaft 40 from the through hole 111 with a diameter smaller than the
diameter of the oil feed hole 42 in the rotation shaft 40. Thus, the oil feed25
component 100 can improve the capacity to supply the refrigerating machine oil 6 to
the sliding parts of the compression mechanism 20 in a state in which the rotation
shaft 40 falls within a low-rotation speed range. That is, the reliability of the
compressor 1 can be ensured in a state in which the rotation shaft 40 falls within a
low-rotation speed range.30
22
[0046]
There is a conventional oil feed component including a main plate portion that
is formed in the same manner as the main plate portion 110 of the oil feed component
100 according to the present Embodiment 1. This conventional oil feed component
has a problem in that it is difficult to attach into the rotation shaft of the compressor.5
In view of that, in the oil feed component 100 according to the present Embodiment 1,
each of the insertion portions 120 has the following configuration.
[0047]
Specifically, each of the insertion portions 120 includes a base end portion 121
and a tip end portion 125. The base end portion 121 is connected to the main plate10
portion 110 at an end portion 122 that is one end portion of the base end portion 121.
The end portion 122 is equivalent to a second end portion. An end portion 126 that
is one end portion of the tip end portion 125 is connected to an end portion 123 that is
the other end portion of the base end portion 121. An end portion 127 that is the
other end portion of the tip end portion 125 is a tip end of the insertion portion 120.15
Note that the end portion 123 is equivalent to a third end portion, the end portion 126
is equivalent to a fourth end portion, and the end portion 127 is equivalent to a fifth
end portion. A location where the end portion 123 of the base end portion 121, and
the end portion 126 of the tip end portion 125 are connected is hereinafter referred to
as a "connection portion 130."20
[0048]
The insertion portions 120, each of which has the configuration as described
above, have such a posture as described below. Note that in the description of the
posture of the insertion portions 120, an imaginary straight line passing through the
through hole 111 on the main plate portion 110 and perpendicular to the main plate25
portion 110 is defined as a first imaginary straight line L1. The first imaginary straight
line L1 is substantially parallel to the rotation center of the rotation shaft 40 when the
oil feed component 100 is attached to the end portion 41 of the rotation shaft 40. In
other words, the first imaginary straight line L1 is substantially parallel to a direction in
which the oil feed hole 42 extends when the oil feed component 100 is attached to the30
23
end portion 41 of the rotation shaft 40. Under the definition of the first imaginary
straight line L1 as described above, in each of the base end portions 121, the end
portion 123 is located at a position furthest from the first imaginary straight line L1.
In each of the tip end portions 125, the end portion 126 is located at a position
furthest from the first imaginary straight line L1. That is, in each of the insertion5
portions 120, the connection portion 130 is located at a position furthest from the first
imaginary straight line L1.
[0049]
In the oil feed component 100 in which each of the insertion portions 120 has
the above posture, it suffices that each connection portion 130 and each end portion10
127 are located in a manner as described below, depending on the diameter of the oil
feed hole 42 in the rotation shaft 40 into which the oil feed component 100 is
attached. This makes it easier to attach the oil feed component 100 into the rotation
shaft 40, compared to the conventional oil feed component.
[0050]15
To be more specific, an imaginary circle that touches the outer surface of the
connection portion 130 of each of the insertion portions 120 is defined as a first
imaginary circle C1. A diameter of the first imaginary circle C1 is defined as a first
diameter D1. In addition, an imaginary circle that touches the outer surface of the
end portion 127 of the tip end portion 125 of each of the insertion portions 120 is20
defined as a second imaginary circle C2. A diameter of the second imaginary circle
C2 is defined as a second diameter D2. A diameter of the oil feed hole 42 formed in
the rotation shaft 40 is defined as a third diameter D3. Under the definitions of the
diameters as described above, it suffices that the first diameter D1 is larger than the
third diameter D3, while the second diameter D2 is smaller than the third diameter25
D3.
[0051]
The reasons why the oil feed component 100 according to the present
Embodiment 1 is attached into the rotation shaft 40 more easily than the conventional
oil feed component are explained below with reference to a schematic diagram of the30
24
oil feed component 100 according to the present Embodiment 1 and schematic
diagrams of oil feed components according to Comparative Examples.
[0052]
Fig. 6 is a schematic diagram illustrating the oil feed component according to
Embodiment 1 when viewed from the side. Figs. 7 and 8 are schematic diagrams,5
each of which illustrates an oil feed component according to Comparative Example
when viewed from the side. Note that Figs. 6 to 8 exemplify a pair of insertion
portions opposite to each other.
[0053]
In each of the insertion portions 120 of the oil feed component 100 according to10
the present Embodiment 1 illustrated in Fig. 6, as described above, in each of the
base end portions 121, the end portion 123 is located at a position furthest from the
first imaginary straight line L1. In each of the tip end portions 125, the end portion
126 is located at a position furthest from the first imaginary straight line L1.
[0054]15
In each of insertion portions 320 of an oil feed component 300 according to
Comparative Example illustrated in Fig. 7, a base end portion 321 is equally
distanced from the first imaginary straight line L1 in its entirety. A tip end portion 325
is also equally distanced from the first imaginary straight line L1 in its entirety. That
is, in the oil feed component 300 according to Comparative Example illustrated in Fig.20
7, the insertion portions 320 extend from a main plate portion 310 parallel to the first
imaginary straight line L1. The insertion portions 320 extend parallel to each other.
Engagement claws of an oil feed component described in Japanese Utility Model
Laid-Open No. S63-154787 disclosed in Citation List have the same shape as the
insertion portions 320 illustrated in Fig. 7.25
[0055]
In each of insertion portions 420 of an oil feed component 400 according to
Comparative Example illustrated in Fig. 8, a base end portion 421 is equally
distanced from the first imaginary straight line L1 in its entirety. In a tip end portion
425, a distance from the first imaginary straight line L1 decreases as the tip end30
25
portion 425 extends from the base end portion 421 toward the tip end. That is, in the
oil feed component 400 according to Comparative Example illustrated in Fig. 8, the
base end portions 421 of the insertion portion 420 extend from a main plate portion
410 parallel to the first imaginary straight line L1. The base end portions 421 of the
insertion portions 420 extend parallel to each other.5
[0056]
When an oil feed component is attached into a rotation shaft, first each of
insertion portions of the oil feed component is inserted into an oil feed hole in the
rotation shaft, such that an outer surface of each of the insertion portions is in contact
with an inner circumferential surface of the rotation shaft. Each of the insertion10
portions is inserted into the oil feed hole until the oil feed component reaches a
specified attachment position. Each of the insertion portions whose outer surface is
in contact with the inner circumferential surface of the rotation shaft is pressed by the
inner circumferential surface of the rotation shaft and becomes deformed. This
causes a spring force to be generated in each of the insertion portions whose outer15
surface is in contact with the inner circumferential surface of the rotation shaft. The
spring force in the insertion portion is a reaction force generated in a deformed
insertion portion when this deformed insertion portion returns to its original shape.
The oil feed component is fixed to the rotation shaft by using the spring force
generated in each of the insertion portions inserted into the oil feed hole in the20
rotation shaft. In the manner as described above, the oil feed component is attached
into the rotation shaft.
[0057]
In the oil feed component 300 according to Comparative Example illustrated in
Fig. 7, each of the insertion portions 320 extends parallel to the first imaginary straight25
line L1. Due to this structure, in a case where the oil feed component 300 according
to Comparative Example illustrated in Fig. 7 is fixed to the rotation shaft 40 in the
manner as described above, a diameter of an imaginary circle that touches the outer
surface of the tip end of each of the insertion portions 320 needs to be larger than the
third diameter D3 that is a diameter of the oil feed hole 42. Therefore, it is difficult for30
26
the oil feed component 300 according to Comparative Example illustrated in Fig. 7 to
insert the tip end of each of the insertion portions 320 into the oil feed hole 42. In the
oil feed component 300 according to Comparative Example illustrated in Fig. 7, each
of the insertion portions 320 is inserted into the oil feed hole 42, while the major
portion of the outer surface of each of the insertion portions 320 is in contact with the5
inner circumferential surface 46 of the rotation shaft 40, until the oil feed component
300 reaches a specified attachment position. For this reason, the oil feed
component 300 according to Comparative Example illustrated in Fig. 7 results in an
increase in resistance caused by inserting each of the insertion portions 320 into the
oil feed hole 42. Therefore, it is difficult to attach the oil feed component 30010
according to Comparative Example illustrated in Fig. 7 into the rotation shaft 40.
[0058]
In the oil feed component 400 according to Comparative Example illustrated in
Fig. 8, in each of tip end portions 425, a distance from the first imaginary straight line
L1 decreases as the tip end portion 425 extends from the base end portion 42115
toward the tip end. Due to this structure, in the oil feed component 400 according to
Comparative Example illustrated in Fig. 8, a diameter of an imaginary circle that
touches the outer surface of the tip end of each of the tip end portions 425 may be
smaller than the third diameter D3 that is a diameter of the oil feed hole 42. The
reason for this is that even though the tip end of each of the tip end portions 425 is20
located at such a position as described above, the outer surface of each of the base
end portions 421 can still be in contact with the inner circumferential surface 46 of the
rotation shaft 40 when the insertion portions 420 are inserted into the oil feed hole 42.
With this structure, it is easier for the oil feed component 400 according to
Comparative Example illustrated in Fig. 8 to insert the tip end of each of the insertion25
portions 420 into the fuel feed hole 42, compared to the oil feed component 300
according to Comparative Example illustrated in Fig. 7.
[0059]
However, in the oil feed component 400 according to Comparative Example
illustrated in Fig. 8, each of the base end portions 421 of the insertion portions 42030
27
extends parallel to the first imaginary straight line L1. Accordingly, in the oil feed
component 400 according to Comparative Example illustrated in Fig. 8, each of the
insertion portions 420 is inserted into the oil feed hole 42, while the major portion of
the outer surface of each of the base end portions 421 is in contact with the inner
circumferential surface 46 of the rotation shaft 40, until the oil feed component 4005
reaches a specified attachment position. For this reason, the oil feed component
400 according to Comparative Example illustrated in Fig. 8 results in an increase in
resistance caused by inserting each of the insertion portions 420 into the oil feed hole
42. Therefore, it is also difficult to attach the oil feed component 400 according to
Comparative Example illustrated in Fig. 8 into the rotation shaft 40 similarly to the oil10
feed component 300 according to Comparative Example illustrated in Fig. 7.
[0060]
In contrast, in the oil feed component 100 according to the present
Embodiment 1, the second diameter D2 of the second imaginary circle C2 that
touches the outer surface of each of the end portions 127, that are the tip ends of the15
insertion portions 120, can be set smaller than the third diameter D3 that is a
diameter of the oil feed hole 42 as described above. With this structure, it is easy for
the oil feed component 100 according to the present Embodiment 1 to insert each of
the end portions 127, that are the tip ends of the insertion portions 120, into the oil
feed hole 42. In this case, in the oil feed component 100 according to the present20
Embodiment 1, the first diameter D1 of the first imaginary circle C1 that touches the
outer surface of each of the connection portions 130 of the insertion portions 120 can
be set larger than the third diameter D3 that is a diameter of the oil feed hole 42 as
described above. With this structure, even when the second diameter D2 is set
smaller than the third diameter D3, it is still possible to attach the oil feed component25
100 according to the present Embodiment 1 into the rotation shaft 40.
[0061]
In the oil feed component 100 according to the present Embodiment 1, each of
the insertion portions 120 is inserted into the oil feed hole 42, while only the outer
surface of the connection portion 130 of each of the insertion portions 120 is in30
28
contact with the inner circumferential surface 46 of the rotation shaft 40, until the oil
feed component 100 reaches a specified attachment position. That is, the
connection portion 130 of each of the insertion portions 120 is in contact with the
inner circumferential surface 46 of the rotation shaft 40, and thereby the oil feed
component 100 is fixed to the rotation shaft 40. Due to this configuration, the oil5
feed component 100 according to the present Embodiment 1 can decrease the
resistance caused by inserting each of the insertion portions 120 into the oil feed hole
42. Therefore, it is easier to attach the oil feed component 100 according to the
present Embodiment 1 into the rotation shaft 40 than the conventional oil feed
components.10
[0062]
Note that in the present Embodiment 1, as illustrated in Fig. 4, each of the
insertion portions 120 is formed in the shape described above by forming inclined
surfaces on the base end portion 121 and on the tip end portion 125. To be more
specific, each of the base end portions 121 includes a first inclined surface portion15
124 connected to the end portion 126 of the tip end portion 125 and approaching the
first imaginary straight line L1 as the base end portion 121 extends from the end
portion 123 toward the end portion 122. Each of the tip end portions 125 includes a
second inclined surface portion 128 connected to the end portion 123 of the base end
portion 121 and approaching the first imaginary straight line L1 as the tip end portion20
125 extends from the end portion 126 toward the end portion 127. Note that the
base end portion 121 may include the first inclined surface portion 124 in its entirety,
or may partially include the first inclined surface portion 124. The tip end portion 125
may include the second inclined surface portion 128 in its entirety, or may partially
include the second inclined surface portion 128. The insertion portion 120 is made25
up of the first inclined surface portion 124 and the second inclined surface portion 128
in the manner as described above, so that the insertion portion 120 is formed easily,
which facilitates manufacturing of the oil feed component 100.
[0063]
29
In a case where the insertion portion 120 is made up of the first inclined surface
portion 124 and the second inclined surface portion 128, it is preferable to set the
angles of the first inclined surface portion 124 and the second inclined surface portion
128 in a manner as described below. With reference to the schematic diagram of
the oil feed component 100 illustrated in Fig. 6, optimal angles of the first inclined5
surface portion 124 and the second inclined surface portion 128 are described below.
[0064]
As illustrated in Fig. 6, an imaginary straight line that touches the outer surface
of the connection portion 130 and extends parallel to the first imaginary straight line
L1 is defined as a second imaginary straight line L2. Under the definition as10
described above, it is preferable that an angle β formed between the second
imaginary straight line L2 and the second inclined surface portion 128 of the tip end
portion 125 is larger than an angle α formed between the second imaginary straight
line L2 and the first inclined surface portion 124 of the base end portion 121. The
reason for this is that it is sufficient that the first inclined surface portion 124 forms15
such an angle relative to the second imaginary straight line L2 that the base end
portion 121 is not in contact with the inner circumferential surface 46 of the rotation
shaft 40 when the insertion portions 120 are inserted into the oil feed hole 42 in the
rotation shaft 40. In contrast, it is preferable that the end portion 127, that is the tip
end of the tip end portion 125, is located at such a position that the second diameter20
D2 is reduced to a minimum to facilitate the insertion into the oil feed hole 42 in the
rotation shaft 40. In view of that, it is preferable that the angle β formed between the
second imaginary straight line L2 and the second inclined surface portion 128 of the
tip end portion 125 is larger than the angle α formed between the second imaginary
straight line L2 and the first inclined surface portion 124 of the base end portion 121.25
[0065]
It is preferable, as illustrated in Figs. 3 to 6, that the oil feed component 100
includes at least one contact portion 140 provided on the outer circumferential portion
112 of the main plate portion 110 and in contact with the end portion 41 of the rotation
shaft 40. Note that in the present Embodiment 1, a total of four contact portions 14030
30
are provided, each of which is located between the insertion portions 120. When
each of the insertion portions 120 is inserted into the oil feed hole 42 in the rotation
shaft 40, the oil feed component 100 stops at a position where the contact portions
140 come into contact with the end portion 41 of the rotation shaft 40. Accordingly,
the oil feed component 100 includes the contact portions 140 to facilitate positioning5
of the oil feed component 100 at the time of attaching the oil feed component 100 into
the rotation shaft 40. In addition, the oil feed component 100 includes the contact
portions 140, so that the oil feed component 100 can be prevented from further
entering the oil feed hole 42 during driving of the compressor 1. Thus, the oil feed
component 100 includes the contact portions 140, to thereby improve the reliability of10
the compressor 1.
[0066]
Note that the number of the insertion portions 120 included in the oil feed
component 100 is not particularly limited, provided that a plurality of the insertion
portions 120 are included. That is, the number of the insertion portions 120 included15
in the oil feed component 100 is equal to or larger than two. However, it is
preferable that the number of the insertion portions 120 is four. It is also preferable
that two of the four insertion portions 120 are located opposite to each other, while the
two remaining insertion portions 120 are located opposite to each other. To be more
specific, the oil feed component 100 is fixed to the rotation shaft 40 by using a spring20
force of the insertion portions 120. Due to this configuration, as the number of the
insertion portions 120 decreases, rigidity of the insertion portions 120 needs to be
increased, and accordingly a greater force is required to deform the insertion portions
120. In other words, a greater force is required to insert the insertion portions 120
into the oil feed hole 42. In contrast, as the number of the insertion portions 12025
increases excessively, a spring force of each of the insertion portions 120 is reduced,
and consequently the oil feed component 100 is fixed to the rotation shaft 40 with
decreased stability. It is preferable to apply a spring force of the insertion portions
120 to the inner circumferential surface 46 of the rotation shaft 40 axisymmetrically
with reference to the axis extending in a direction in which the oil feed hole 42 is30
31
formed, such that the oil feed component 100 is fixed to the rotation shaft 40 in a
stable manner. That is, it is preferable that two insertion portions 120 are located
opposite to each other. Accordingly, it is preferable that the oil feed component 100
includes four insertion portions 120. It is also preferable that two of the four insertion
portions 120 are located opposite to each other, while the two remaining insertion5
portions 120 are located opposite to each other.
[0067]
The oil feed component 100 according to the present Embodiment 1 described
above is provided in the compressor 1 including the rotation shaft 40 in which the oil
feed hole 42 is formed and opened at the end portion 41 to supply the refrigerating10
machine oil 6 suctioned into the oil feed hole 42 to the compression mechanism 20.
The oil feed component 100 includes the main plate portion 110 and the plurality of
insertion portions 120. The through hole 111 is formed on the main plate portion
110. Each of the insertion portions 120 protrudes from the main plate portion 110 at
a position near the outer circumferential portion 112 of the main plate portion 11015
relative to the through hole 111. Each of the insertion portions 120 is inserted into
the oil feed hole 42. Each of the insertion portions 120 includes the base end portion
121 and the tip end portion 125. The base end portion 121 is connected to the main
plate portion 110 at the end portion 122. The tip end portion 125 is connected to the
end portion 123 of the base end portion 121 at the end portion 126. The end portion20
127 of the tip end portion 125 is a tip end of the insertion portion 120. In a case
where an imaginary straight line passing through the through hole 111 and
perpendicular to the main plate portion 110 is defined as the first imaginary straight
line L1, in each of the base end portions 121, the end portion 123 is located at a
position furthest from the first imaginary straight line L1. In each of the tip end25
portions 125, the end portion 126 is located at a position furthest from the first
imaginary straight line L1. In each of the insertion portions 120 of the oil feed
component 100, the connection portion 130 is in contact with the inner circumferential
surface 46 of the rotation shaft 40, and thereby the oil feed component 100 is fixed to
the rotation shaft 40, the connection portion 130 being a location where the end30
32
portion 123 of the base end portion 121, and the end portion 126 of the tip end portion
125 are connected.
[0068]
It is easy for the oil feed component 100 having the configuration as described
above to insert each of the end portions 127, that are the tip ends of the insertion5
portions 120, into the oil feed hole 42. The oil feed component 100 having the
configuration as described above can also decrease the resistance caused by
inserting each of the insertion portions 120 into the oil feed hole 42. Therefore, it is
easier to attach the oil feed component 100 having the configuration as described
above into the rotation shaft 40 than the conventional oil feed components.10
[0069]
Embodiment 2
The oil feed component 100 has a configuration as described below, such that
the number of components of the compressor 1 can be reduced as compared to
Embodiment 1, and it is thus possible to reduce the assembly man-hours for the15
compressor 1. Note that items that are not particularly described in the present
Embodiment 2 are the same as those in Embodiment 1, and the same functions and
configurations as those in Embodiment 1 are denoted by the same reference
numerals and described below.
[0070]20
Fig. 9 is a vertical cross-sectional view illustrating the oil feed component
according to Embodiment 2. Fig. 10 is a bottom view illustrating the oil feed
component according to Embodiment 2.
In the oil feed component 100 according to the present Embodiment 2, one of
the insertion portions 120 is provided with a vane portion 145 formed by twisting a25
plate-like part and connected to the end portion 127 of the tip end portion 125.
[0071]
To be more specific, a third imaginary straight line L3 illustrated in Figs. 9 and
10 shows a position of the center of the oil feed hole 42 when the oil feed component
100 is attached into the rotation shaft 40. The shape of the vane portion 145 that is30
33
a plate-like part is viewed from its one end portion near the end portion 127 of the
insertion portion 120 toward the other end portion opposite to the one end portion.
In this case, the vane portion 145 extends from the end portion 127 of one of the
insertion portions 120 toward the third imaginary straight line L3. The vane portion
145 is also bent at a position on the third imaginary straight line L3, and thereafter5
extends along the third imaginary straight line L3. The vane portion 145 that is a
plate-like part is twisted at a point from which the vane portion 145 extends along the
third imaginary straight line L3. When the oil feed component 100 is attached into
the rotation shaft 40, the twisted point of the vane portion 145 is located within the oil
feed hole 42 to serve as a centrifugal pump.10
[0072]
That is, the oil feed component 100 according to the present Embodiment 2
has such a configuration that the centrifugal pump is formed integrally with the oil
feed component 100. Accordingly, the compressor 1 provided with the oil feed
component 100 according to the present Embodiment 2 does not need the centrifugal15
pump 45 illustrated in Embodiment 1. Therefore, the number of components of the
compressor 1 can be reduced by employing the oil feed component 100 according to
the present Embodiment 2. In addition, simultaneously with attaching the oil feed
component 100 according to the present Embodiment 2 into the rotation shaft 40, the
centrifugal pump is also installed in the rotation shaft 40. Consequently, the20
assembly man-hours for the compressor 1 can also be reduced by employing the oil
feed component 100 according to the present Embodiment 2.
Reference Signs List
[0073]
1: compressor, 2A: first suction pipe, 2B: second suction pipe, 3: suction25
muffler, 4: discharge pipe, 6: refrigerating machine oil, 10: compressor outer shell, 11:
head portion, 12: body portion, 13: bottom portion, 20: compression mechanism, 21A:
first cylinder, 21B: second cylinder, 22A: first piston, 22B: second piston, 23A: first
muffler, 23B: second muffler, 24A: upper bearing, 24B: lower bearing, 25: partition
plate, 30: rotating electric machine, 31: rotor, 32: stator, 40: rotation shaft, 41: end30
34
portion, 42: oil feed hole, 43: first oil feed port, 44: second oil feed port, 45: centrifugal
pump, 46: inner circumferential surface, 100: oil feed component, 110: main plate
portion, 111: through hole, 112: outer circumferential portion, 120: insertion portion,
121: base end portion, 122: end portion, 123: end portion, 124: first inclined surface
portion, 125: tip end portion, 126: end portion, 127: end portion, 128: second inclined5
surface portion, 130: connection portion, 140: contact portion, 145: vane portion, 200:
refrigeration cycle device, 201: four-way switching valve, 202: outdoor side heat
exchanger, 203: pressure-reducing device, 204: indoor side heat exchanger, 300: oil
feed component (Comparative Example), 310: main plate portion (Comparative
Example), 320: insertion portion (Comparative Example), 321: base end portion10
(Comparative Example), 325: tip end portion (Comparative Example), 400: oil feed
component (Comparative Example), 410: main plate portion (Comparative Example),
420: insertion portion (Comparative Example), 421: base end portion (Comparative
Example), 425: tip end portion (Comparative Example), C1: first imaginary circle, C2:
second imaginary circle, D1: first diameter, D2: second diameter, D3: third diameter,15
L1: first imaginary straight line, L2: second imaginary straight line, L3: third imaginary
straight line
35
WE CLAIM:
[Claim 1]
An oil feed component provided in a compressor including a rotation shaft in
which an oil feed hole is formed to supply refrigerating machine oil suctioned into the
oil feed hole to a compression mechanism, the oil feed hole being opened at a first5
end portion, the first end portion being one end portion of the rotation shaft, the oil
feed component comprising:
a main plate portion on which a through hole is formed; and
a plurality of insertion portions, each of which protrudes from the main plate
portion at a position near an outer circumferential portion of the main plate portion10
relative to the through hole, the plurality of insertion portions being inserted into the oil
feed hole, wherein
each of the insertion portions includes
a base end portion connected to the main plate portion at a second end
portion, the second end portion being one end portion of the base end portion, and15
a tip end portion connected to a third end portion at a fourth end portion, the
third end portion being an other end portion of the base end portion, the fourth end
portion being one end portion of the tip end portion, the tip end portion having a fifth
end portion, the fifth end portion being an other end portion of the tip end portion, the
fifth end portion being a tip end of the insertion portion,20
where an imaginary straight line passing through the through hole and
perpendicular to the main plate portion is defined as a first imaginary straight line,
in each of the base end portions, the third end portion is located at a position
furthest from the first imaginary straight line, and
in each of the tip end portions, the fourth end portion is located at a position25
furthest from the first imaginary straight line, and
in each of the insertion portions, a connection portion is in contact with an inner
circumferential surface of the rotation shaft, and thereby the oil feed component is
fixed to the rotation shaft, the connection portion being a location where the third end
36
portion of the base end portion, and the fourth end portion of the tip end portion are
connected.
[Claim 2]
The oil feed component of claim 1, wherein
where5
an imaginary circle touching an outer surface of the connection portion of each
of the insertion portions is defined as a first imaginary circle,
a diameter of the first imaginary circle is defined as a first diameter,
an imaginary circle touching an outer surface of the fifth end portion of the tip
end portion of each of the insertion portions is defined as a second imaginary circle,10
a diameter of the second imaginary circle is defined as a second diameter, and
a diameter of the oil feed hole formed in the rotation shaft is defined as a third
diameter,
the first diameter is larger than the third diameter,
the second diameter is smaller than the third diameter.15
[Claim 3]
The oil feed component of claim 1 or 2, comprising a contact portion provided
at the outer circumferential portion of the main plate portion and in contact with the
first end portion of the rotation shaft.
[Claim 4]20
The oil feed component of any one of claims 1 to 3, wherein
each of the base end portions includes a first inclined surface portion
connected to the fourth end portion of the tip end portion and approaching the first
imaginary straight line as the base end portion extends from the third end portion
toward the second end portion,25
each of the tip end portions includes a second inclined surface portion
connected to the third end portion of the base end portion and approaching the first
imaginary straight line as the tip end portion extends from the fourth end portion
toward the fifth end portion, and
37
where an imaginary straight line touching an outer surface of the connection
portion and parallel to the first imaginary straight line is defined as a second
imaginary straight line,
an angle formed between the second imaginary straight line and the second
inclined surface portion is larger than an angle formed between the second imaginary5
straight line and the first inclined surface portion.
[Claim 5]
The oil feed component of any one of claims 1 to 4, comprising four of the
insertion portions, wherein
two of the insertion portions are located opposite to each other, and10
remaining two of the insertion portions are located opposite to each other.
[Claim 6]
The oil feed component of any one of claims 1 to 5, wherein one of the
insertion portions is provided with a vane portion formed by twisting a plate-like part
and connected to the fifth end portion.15
[Claim 7]
A compressor comprising:
a rotating electric machine;
a rotation shaft connected to the rotating electric machine to rotate using power
of the rotating electric machine;20
a compression mechanism connected to the rotation shaft, and configured to
compress refrigerant suctioned from an exterior by using power of the rotating electric
machine transmitted through the rotation shaft;
a compressor outer shell inside which refrigerating machine oil is retained, the
compressor outer shell having the rotating electric machine, the rotation shaft, and25
the compression mechanism accommodated therein; and
the oil feed component of any one of claims 1 to 6, wherein
in the rotation shaft, an oil feed hole is formed and opened at one end portion
of the rotation shaft to supply the refrigerating machine oil suctioned into the oil feed
hole to the compression mechanism, and30
38
each of the insertion portions of the oil feed component is inserted into the oil
feed hole, the connection portion of each of the insertion portions is in contact with
the inner circumferential surface of the rotation shaft, and thereby the oil feed
component is fixed to the rotation shaft.
[Claim 8]5
A refrigeration cycle device comprising:
the compressor of claim 7;
a radiator through which refrigerant compressed by the compressor transfers
heat;
a pressure-reducing device configured to reduce a pressure of the refrigerant10
flowing out from the radiator; and
an evaporator through which the refrigerant flowing out from the pressure-
reducing device evaporates.