DESCRIPTION
TITLE OF INVENTION: HERMETIC TYPE COMPRESSOR
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is based on and claims the benefit of priority from Japanese Patent Application No. 2011-005917, filed in Japan on January 14,2011, the content of which is incorporated herein by reference in its entirety.
Technical Field
[0001 ] The present invention relates to a hermetic type compressor. More
specifically, the present invention relates to minimization of pressure loss of a suction
accumulator.
Background Art
[0002] Conventionally, in order to perform gas-liquid separation of suctioned
refrigerant gas, and to ensure a capacity for accumulating the separated liquid
refrigerant including refrigerant oil, it is proposed a suction accumulator of a hermetic
type compressor wherein an outflow pipe and an inflow pipe are inserted in a body
having a cylindrical shape so as to reach inside of the body (for example, see Patent
literature 1).
Citation List
Patent Literature
[0003] Patent literature 1: JP 2009-162222 A (Fig. 8)
Summary of Invention
Technical Problem

[0004] The suction accumulator having the functions of performing gas-liquid separation of suctioned refrigerant gas, and of accumulating the separated liquid including refrigerant oil, provided to the conventional hermetic type compressor, is limited by a volume of the body, a diameter of the piping in a main body of an air conditioner, and a diameter of a suction engaging section of a compression chamber in the compressor that can fulfill the functions. Therefore, the suction accumulator has the following problems.
(1) Sudden enlargement loss of refrigerant gas which passes through the body of the suction accumulator from the inflow pipe equipped in the suction accumulator, and which is then made to flow in the outflow pipe equipped to the suction accumulator and to be taken in from the suction engaging section of the compression chamber in the compressor becomes extraordinary large when the refrigerant gas flows in the body of the suction accumulator from the inflow pipe.
(2) Sudden contraction loss of the refrigerant gas becomes extraordinary large when the refrigerant gas flows in the outflow pipe after passing through the body of the suction accumulator.
[0005] Therefore, since suction efficiency of the refrigerant gas is decreased, the pressure of the refrigerant gas that is taken in the compressor is reduced, and the compression work increases more than an ideal pressure state of a refrigeration cycle. This leads to a reduction in compressor efficiency, and further to reduction of pressure in an evaporator equipped in the main body of the air conditioner, and a decrease in refrigeration cycle efficiency.
[0006] The present invention aims to solve the above-mentioned problems. The present invention aims to provide a hermetic type compressor that can improve suction efficiency of refrigerant gas by minimizing pressure loss of the refrigerant gas when the

refrigerant gas passes through the suction accumulator. Solution to Problem
[0007] The hermetic type compressor according to the present invention is a hermetic type compressor including a suction accumulator provided at a side part of a hermetic container. (1) The suction accumulator includes an inflow pipe being a straight pipe with a constant inner diameter, whereto a refrigerant piping in a refrigeration cycle is connected. (2) The suction accumulator also includes a body having a cylindrical shape as a whole, whose both ends are narrowed. The body is formed with a predetermined diameter so as to have a capacity that fulfills a function of performing a gas-liquid separation of suctioned refrigerant gas, and of accumulating separated liquid refrigerant including refrigerant oil. An end part of the body on a side of the inflow pipe is formed in a diffuser shape with a predetermined spread angle, and a diffuser shape part of the body is formed smoothly in a curve convex to an inner side and is connected to the inflow pipe. (3) The suction accumulator also includes at least one piece of an outflow pipe having an inflow port with a diameter larger than a diameter of the inflow pipe, or an inflow port with a bell-mouth shape. Advantageous Effects of Invention
[0008] In the hermetic type compressor according to the present invention, the inflow pipe of the suction accumulator is connected to the body wherein the end part on the inflow pipe side is formed in the diffuser shape with the predetermined spread angle, and the diffuser shape part is formed smoothly in the curve convex to the inner side, and at least one piece of the outflow pipe whose diameter of the inflow port is larger than the diameter of the inflow pipe, or whose inflow port has the bell-mouth shape, is included. Thus, by minimizing the pressure loss of refrigerant gas at the time when the refrigerant gas passes through the suction accumulator, the suction efficiency of the

refrigerant gas is improved. Further, since the pressure of the refrigerant gas that is taken in the hermetic type compressor is improved, and the compression work comes close to the ideal pressure state of the refrigeration cycle, the compressor efficiency is increased. Additionally, by improving the pressure in the evaporator in the — ■•■ refrigeration cycle, mere is an effect to improve the refrigeration cycle efficiency. Brief Description of Drawings
[0009] The present invention will become fully understood from the detailed description given hereinafter in conjunction with the accompanying drawings, in which:
Fig. 1 is a diagram describing the first embodiment, and is a longitudinal sectional view describing an overall structure of a hermetic type compressor 100;
Fig. 2 is a diagram describing the first embodiment, and is a diagram describing a part of a suction accumulator 1 in section;
Fig. 3 is an enlarged view of Apart in Fig. 2;
Fig. 4 is a diagram describing the first embodiment, and is a diagram describing a part of a suction accumulator 1-1 as a variation in section;
Fig. 5 is a diagram describing the first embodiment, and is a diagram describing a relation between a spread angle in a gently broadening pipe and pressure loss;
Fig. 6 is a diagram describing the first embodiment, and is a diagram describing a relation between a diameter of an outflow pipe and pressure loss;
Fig. 7 is a diagram describing the first embodiment, and is a refrigerant circuit diagram of an air conditioner;
Fig. 8 is a diagram describing the first embodiment, and is an exploded perspective view of an outdoor unit 300 of the air conditioner;
Fig. 9 is a diagram shown for comparison, and is a longitudinal sectional view

describing an overall structure of a general hermetic type compressor 200; and
Fig. 10 is a diagram shown for comparison, and is a diagram describing a part of a suction accumulator 21 of the general hermetic type compressor 200 in section. Description of Embodiments
In describing preferred embodiments illustrated in the drawings, specific terminology is employed for the sake of clarity. However, the disclosure of the present invention is not intended to be limited to the specific terminology so selected, and it is to be understood that each specific element includes all technical equivalents that operate in a similar manner and achieve a similar result. [0010] Embodiment 1
The hermetic type compressor according to the present embodiment includes a suction accumulator, wherein an inflow pipe formed of a straight pipe, which is connected to a main body of an air conditioner, is connected to the body of the suction accumulator of the predetermined diameter, having a capacity that fulfills a function of performing gas-liquid separation of suctioned refrigerant gas and accumulating separated liquid refrigerant including refrigerant oil, with a spread angle having a diffuser effect and a smooth curve shape that is convex to the inner side. The suction accumulator is equipped with at least one piece of an outflow pipe wherein a diameter of an inflow port is preferably increased, and a diameter of a pipe is reduced in an engaging section of a suction port in a compression chamber in a compression element. [0011 ] In the hermetic type compressor of the present embodiment, the inflow pipe that is connected to the main body of the air conditioner is a straight pipe including one projection shape (stopper) extending toward the inner side for minimizing pressure loss while limiting a position of a refrigerant piping that is connected from the main body of the air conditioner. The spread angle having the diffusion effect and the smooth curve

shape that is convex to the inner side have a spread angle of 10 to 60 degrees from the outlet section in the inflow pipe, and are smoothly connected to the body of the suction accumulator, so as to minimize the pressure loss of the refrigerant gas passing through the spread angle and the curve shape. In order to minimize contraction loss at the time when the refrigerant gas that has passed through the smooth curve shape convex to the inner side flows in an inlet of the outflow pipe in the suction accumulator, and to fulfill the function of accumulating liquid refrigerant including refrigerant oil, from which suctioned refrigerant gas is separated, the hermetic type compressor including the suction accumulator is equipped with at least one piece of an outflow pipe wherein the outer diameter of the inlet of the outflow pipe in the suction accumulator is larger than the diameter of the inflow pipe in the suction accumulator, and the diameter of the outflow pipe is reduced at least one position so that the diameter of the outflow pipe is made to fit the engaging section of the suction port in the compression chamber of the compressor from the inlet diameter of the outflow pipe in the suction accumulator. [0012] In the hermetic type compressor of the present embodiment, the tip end (inflow port) of the outflow pipe, which is equipped at least one in the suction accumulator, may be a bell-mouth shaped inflow port to minimize sudden contraction loss at the time when the refrigerant gas flows in the outflow pipe, and the bell-mouth shape has an external diameter larger than the diameter of the inflow pipe in the suction accumulator. [0013] Fig. 1 is the diagram describing the first embodiment, and the longitudinal sectional view describing the overall structure of the hermetic type compressor 100. The hermetic type compressor 100 will be described with reference to Fig. 1. [0014] The hermetic type compressor 100 shown in Fig. 1 is a one-cylindered rotary compressor. In the hermetic type compressor 100, a compression element 101 for compressing refrigerant and an electric motor element 102 for activating the

compression element 101 are housed inside the hermetic container 110, and refrigerant
oil for lubricating a sliding part in the compression element 101 is accumulated in the
bottom of the hermetic container 110.
[0015] In the compression element 101 for compressingthe refrigerant, a rolling
piston that engages with an eccentric portion of a rotary shaft rotates inside a cylinder
whose both ends in an axial direction are blocked by two top and bottom bearings. In
the cylinder, a vane that is provided in a freely movable manner in a radial direction is
placed so as to contact with the rolling piston constantly. The refrigerant is
compressed in the compression chamber that is surrounded by an inner periphery of the
cylinder, an outer periphery of the rolling piston, the vane and two bearings.
[0016] As the electric motor element 102 for driving the compression element 101 via
the rotary shaft, a brushless DC motor, or an induction motor, etc. are used.
[0017] The refrigerant compressed in the compression element 101 is discharged into
the hermetic container 110, then passes through the electric motor element 102 and
flows out to a high-pressure side of the refrigerant circuit, which is not shown, from a
discharge pipe 130.
[0018] The electric motor element 102 is powered by a commercial power supply via a
glass terminal 120 that is fixed to the hermetic container 110.
[0019] The hermetic type compressor 100 is equipped with the suction accumulator 1
in its side part. The present embodiment is characterized in the structure of the suction
accumulator 1. Thus, the suction accumulator 1 will be described below in detail.
[0020] Fig. 2 is the diagram describing the first embodiment, and is the diagram
describing a part of the suction accumulator 1 in section. Fig. 3 is the enlarged view of
A part in Fig. 2. The suction accumulator 1 will be described with reference to Fig. 1
through Fig. 3.

*
t
[0021] The suction accumulator 1 is composed of the following elements. (1) Body 5: The overall shape is cylindrical (for example, circular in cross-section), whose both ends are narrowed. The body 5 has a certain diameter so as to have a capacity that fulfills the function of performing gas-liquid separation of suctioned refrigerant gas and accumulating separated liquid refrigerant including refrigerant oil. An end part on a side of an inflow pipe 2 in the body 5 as will be described below has a diffuser (diffusor) shape. In a diffusion pipe being a pipe whose cross sectional area gradually increases, speed and Mach number decrease and pressure increases in a case of supersonic speed (M<1, M is Mach number). Such a pipe is called diffuser. Further, a diffuser shape part 6 of the body 5 in the present embodiment is formed smoothly in a curve (for example, a circular arc) convex to the inner side. The spread angle (see Fig. 2) of the diffuser shape part 6, which will be described in detail, is preferably 10 to 60 degrees. The spread angle describes the extent of the cross sectional area. When a cross sectional area does not change, the angle is 0 degree. Meanwhile, as in a general suction accumulator 21 as shown in Fig. 10, in a case wherein a cross sectional area increases abruptly when entering into the body from the inflow pipe, the spread angle is approximately 180 degrees. [0022] (2) Inflow pipe 2: A straight pipe of a constant inner diameter, whereto a refrigerant piping of a unit (for example, an outdoor unit of an air conditioner) is connected. The body 5 is connected with the inflow pipe 2 smoothly by the diffuser shape part 6 (the spread angle (10 to 60 degrees) having a diffuser effect, and a smooth curve (for example, a circular arc) convex to the inner side). The inflow pipe 2 includes inside itself at least one projection shape part 2a that projects to the inner side. By the projection shape part 2a, it is possible to minimize the pressure loss at the time when refrigerant gas passes through the inflow pipe 2 while fulfilling limitation

(positioning) of the refrigerant piping of the unit (for example, the outdoor unit of the
air conditioner). In the inflow pipe of the general suction accumulator 21 (see Fig. 10),
since a part of a straight pipe is narrowed (the diameter is reduced), and the position of
the refrigerant piping in the unit is limited, pressure loss exists at the time when
refrigerant gas passes through the inflow pipe.
[0023] (3) Outflow pipe 3: An outflow part 8 of the outflow pipe 3 in the suction
accumulator 1 has a diameter that fits the compression chamber suction port engaging
section 4 of the hermetic type compressor 100 (the diameter is reduced). An oil
returning hole 10 is formed in a lower part of the outflow pipe 3 inside the body 5 for
returning refrigerant oil to the hermetic type compressor 100. A diameter of an inflow
port 7 of the outflow pipe 3 is larger than the diameter of the inflow pipe 2.
[0024] (4) Ring member 9: The ring member 9 is fitted to an approximately center part
of the body 5. The ring member 9 has an effect to increase intense of the body 5, and
has a role to fix the suction accumulator 1 to the hermetic container 110.
[0025] The hermetic type compressor 100 is mounted on, for example, an outdoor unit
of a main body of an air conditioner. A piping (the piping of the unit) wherein
refrigerant gas that is made into a gaseous state by being evaporated in a heat exchanger
(an outdoor heat exchanger (while heating) or an indoor heat exchanger (while cooling))
flows is connected to the inflow pipe 2 of the suction accumulator 1, which is attached
to a side surface of the hermetic type compressor 100 (see Fig. 3).
[0026] One example of the air conditioner will be described with reference to Fig. 7
and Fig. 8.
[0027] Fig. 7 and Fig. 8 are diagrams describing the first embodiment. Fig. 7 is the
refrigerant circuit diagram of the air conditioner. Fig. 8 is the exploded perspective
view describing the outdoor unit 300 of the air conditioner.

[0028] As shown in Fig. 7, the refrigerant circuit of the air conditioner makes up a refrigeration cycle by sequentially connecting the hermetic type compressor 100 for compressing refrigerant, a four-way valve 52 for switching flowing directions of the refrigerant between the cooling operation and the heating operation, an outdoor side heat exchanger 53 for operating as a condenser during the cooling operation, and as an evaporator during the heating operation, a decompression device 54 (an electronically controlled type expansion valve) for decompressing high-pressure liquid refrigerant to make air-liquid two-phase refrigerant of low-pressure, and an indoor side heat exchanger 55 for operating as an evaporator during the cooling operation, and as a condenser during the heating operation.
[0029] A solid arrow in Fig. 7 indicates a flowing direction of refrigerant during the cooling operation. Further, a dotted line in Fig. 7 indicates a flowing direction of refrigerant during the heating operation.
[0030] An outdoor side blower 56 is provided in the outdoor side heat exchanger 53. An indoor side blower 57 (a transverse fan) is provided in the indoor side heat exchanger 55.
[0031 ] During the cooling operation, refrigerant of high temperature and high pressure that is compressed is discharged from the hermetic type compressor 100, and flows into the outdoor side heat exchanger 53 via the four-way valve 52. In the outdoor side heat exchanger 53, air outside a room is heat exchanged with refrigerant while passing through fins and a tube (a heat exchanger tube) of the outdoor side heat exchanger 53 by the outdoor side blower 56 that is placed in the air trunk of the outdoor side heat exchanger 53, and the refrigerant is cooled to be in a high pressure liquid state. The outdoor side heat exchanger 53 acts as a condenser. After that, the refrigerant passes through the decompression device 54, and is decompressed to be an air-liquid two-phase

refrigerant of low pressure, and then flows in the indoor side heat exchanger 55. In the indoor side heat exchanger 55, air inside a room passes through fins and a tube (a heat exchanger tube) of the indoor side heat exchanger 55 by activating the indoor side blower 57 (the traverse fan) that is placed in the air trunk of the indoor side heat exchanger 55, and is heat exchanged with the refrigerant. In this way, air that is blown into an indoor space is cooled. Meanwhile, the refrigerant receives heat from air and evaporates to be in a gaseous state (the indoor side heat exchanger 55 acts as an evaporator), and then the refrigerant returns to the hermetic type compressor 100. The indoor space is air conditioned (cooled) by the air that is cooled by the indoor side heat exchanger 55.
[0032] During the heating operation, refrigerant flows in an opposite direction to a flow of the refrigerant during the cooling operation in the refrigeration cycle by reversing the four-way valve 52. The indoor side heat exchanger 55 acts as a condenser, and the outdoor side heat exchanger 53 acts as an evaporator. The indoor space is air conditioned (heated) by the air that is heated by the indoor side heat exchanger 55.
[0033] The structure of the outdoor unit 300 of the air conditioner will be described by Fig. 8. The outdoor unit 300 of the air conditioner is composed of the outdoor side heat exchanger 53 in an approximately L-shape by planer view, a bottom plate 68 (base) that forms a bottom part of a chassis of the outdoor unit 300, a plated top panel 59 that forms a top surface of the chassis, a front panel 60 in an approximately L-shape by planer view that forms a front surface and one side part of the chassis, a side panel 61 that forms the other side part of the chassis, a separator 62 that separates an air trunk (a blower chamber) and a machine chamber, an electrical item box 63 for storing electrical items, the hermetic type compressor 100 for compressing refrigerant, refrigerant piping

and refrigerant circuit components 64 that form the refrigerant circuit, the outdoor side blower 56 for sending air to the outdoor side heat exchanger 53, and so on. [0034] By mounting the hermetic type compressor 100 of the present embodiment on the outdoor unit 300 of the air conditioner composed as mentioned above, the compression work comes close to the ideal pressure state of the refrigeration cycle. Thus, a compressor efficiency is improved. Additionally, by improving the pressure in the evaporator equipped in the main body of the air conditioner, there is an effect to improve the refrigeration cycle efficiency.
[0035] Refrigerant gas passes through the inside of the suction accumulator 1 from the inflow pipe 2 of the suction accumulator 1, and then passes through the outflow pipe 3 of the suction accumulator, and flows into the hermetic type compressor 100 from the compression chamber suction port engaging section 4 of the hermetic type compressor 100. Then, the refrigerant gas is adiabatically compressed in the compression chamber of the hermetic type compressor 100, and is discharged from the discharge pipe 130 in the upper part of the hermetic type compressor 100 that is connected to the main body of the air conditioner. The discharged refrigerant gas repeats a cycle of being condensed (the outdoor heat exchanger (cooling)) and evaporated (the indoor heat exchanger (heating)) by heat exchange with surrounding air by the heat exchanger inside the main body of the air conditioner, and being flown in again from the inflow pipe 2 of the suction accumulator 1 that is provided in the side surface of the hermetic type compressor 100.
[0036] Since the refrigerant that flows in the suction accumulator 1 is not completely evaporated in the heat exchanger, and refrigerant oil necessary for lubricating a machine component (the sliding part) in the compression element 101 that is retained inside of the hermetic type compressor 100 is discharged in a state of being mixed in the

refrigerant during the adiabatic compression step, gaseous refrigerant, liquid refrigerant, and the refrigerant oil are in a mixed state.
[0037] When a great amount of liquid refrigerant component in a fluid mixture wherein gaseous refrigerant, liquid refrigerant and the refrigerant oil are mixed flows inside the compression chamber of the hermetic type compressor 100, the refrigerant oil attached to the machine component (the sliding part) in the compression element 101 blends in the liquid refrigerant, and normal lubrication of the machine component (the sliding part) in the compression element 101 is impaired.
[0038] For this reason, the hermetic type compressor 100 is equipped with the suction accumulator 1 in its side. The suction accumulator 1 separates the fluid mixture of gaseous refrigerant, liquid refrigerant and the refrigerant oil flowing inside of the suction accumulator 1 into gaseous refrigerant, and liquid refrigerant/refrigerant oil. The gaseous refrigerant is flown in the main body of the hermetic type compressor 100 through the outflow pipe 3 of the suction accumulator 1. By making the liquid refrigerant and the refrigerant oil retained in the body 5 of the suction accumulator 1, the liquid refrigerant component is prevented from flowing inside the compression chamber of the hermetic type compressor 100 in large quantity. [0039] The retained refrigerant oil is accumulated in the lower part since the refrigerant oil is denser than the liquid refrigerant. Therefore, only the refrigerant oil flows gradually into the main body of the hermetic type compressor 100 from the oil returning hole 10 located in the lower part of the outflow pipe 3 of the suction accumulator 1. Since the retained liquid refrigerant gradually vaporizes and is accumulated in the upper part of the suction accumulator 1, the liquid refrigerant flows into the outflow pipe 3 of the suction accumulator 1. [0040] In the suction accumulator 1, the inflow pipe 2 being the straight pipe

connected to the main body of the air conditioner is smoothly connected, by the spread angle having the diffuser effect and the curve (for example, the circular arc) convex to the inner side, to the body 5 of the suction accumulator 1 of the predetermined diameter so as to have the capacity that fulfills the functions of performing gas-liquid separation of suctioned refrigerant gas, and accumulating the separated liquid refrigerant including refrigerant oil.
[0041] The suction accumulator 1 includes at least one piece of the outflow pipe 3 wherein the diameter of the inflow port 7 is larger than the diameter of the inflow pipe 2 in the suction accumulator 1, and which includes the outflow part 8 that engages with the compression chamber suction port engaging section 4, whose diameter is reduced its size.
[0042] The inflow pipe 2 that is connected to the main body of the air conditioner (the refrigerant piping of the unit) is a straight pipe for minimizing the pressure loss. The diffuser shape part 6 with the spread angle having the diffuser effect and the curve (for example, the circular arc) convex to the inner side minimizes expansion loss of the refrigerant gas passing through the diffuser shape part 6. Further, the diffuser shape part 6 has the spread angle of 10 to 60 degrees from the outlet part of the inflow pipe 2, being smoothly connected to the body 5 in order to form a positive flow directed in the direction of the outer diameter of the body 5, and to make separation of vapor and liquid more efficient. The inflow port 7 of the outflow pipe 3 has a diameter larger than the diameter of the inflow pipe 2 for minimizing contraction loss at the time when refrigerant gas passing through the diffuser shape part 6 having the curve (for example, the circular arc) convex to the inner side flows into the inflow port 7 of the outflow pipe 3 in the suction accumulator 1, and for fulfilling the function of accumulating liquid refrigerant including the refrigerant oil from which suctioned refrigerant gas is

separated. The diameter of the outflow pipe 3 is reduced, from the diameter of the inflow port 7 of the outflow pipe 3, in at least one part of the outflow part 8 that engages with the compression chamber suction port engaging section 4 in the end part on the opposite side to the inflow port 7 so that the diameter of the outflow pipe 3 in that part fits the compression chamber suction port engaging section 4. The suction accumulator 1 includes at least one piece of the outflow pipe 3. [0043] Fig. 4 describes the first embodiment. Fig. 4 is the diagram describing a part of the suction accumulator 1-1 as a variation in section. In the suction accumulator 1-1 as the variation, only an outflow pipe 3-1 is different from, and the others are the same as in the suction accumulator 1 that is shown in Fig. 2. In the outflow pipe 3-1 of the suction accumulator 1-1 as a variation, an inflow port 7-1 is in a bell-mouth shape. By forming the inflow port 7-1 of the outflow pipe 3-1 in the bell-mouth shape, the gas refrigerant component flows in the outflow pipe 3-1 without being impaired the smooth flow.
[0044] Next, operations will be described. In the suction accumulator 1 or 1-1 (hereinafter also referred to simply as the suction accumulator 1) of the present embodiment, as described above, the body 5 of the suction accumulator 1 is smoothly connected to the inflow pipe 2 provided in the suction accumulator 1 by the diffuser shape part 6 with the spread angle having the diffuser effect, and the curve (for example, the circular arc) convex to the inner side. Therefore, refrigerant gas flowing into the suction accumulator 1 provided to the hermetic type compressor 100 from the main body of the air conditioner passes through the suction accumulator 1 with minimizing separation of the refrigerant gas flow.
[0045] Since a positive flow directed in the direction of the outer diameter of the body 5 in the suction accumulator 1 is formed, separation of liquid and vapor of the suctioned

refrigerant gas is performed efficiently. The liquid refrigerant component including the refrigerant oil is accumulated in the lower part of the body 5 in the suction accumulator 1 after flowing along the outer diameter side of the body 5 in the suction accumulator 1. A flow of the gaseous refrigerant component directed to the inflow port 7 or 7-1 (hereinafter also referred to simply as the inflow port 7) of the outflow pipe 3 or 3-1 (hereinafter also referred to simply as the outflow pipe 3) that is provided in the suction accumulator 1 is formed while keeping its smooth flow. [0046] The inflow port 7 in the outflow pipe 3 that is provided in the suction accumulator 1 is in a circular shape or a bell-mouth shape with an outer diameter larger than the diameter of the inflow pipe 2. Therefore, the gaseous refrigerant component flows into the outflow pipe 3 without its smooth flow being impaired. The diameter of the outflow part 8 in the outflow pipe 3 is reduced its size so as to rninimize pipe friction loss inside the outflow pipe 3, and to fit the compression chamber suction port engaging section 4 of the hermetic type compressor 100. Therefore, the refrigerant gas flows in the compression chamber suction port engaging section 4 of the hermetic type compressor 100 with keeping its smooth flow.
[0047] The inflow pipe 2 being the straight pipe that is provided in the suction accumulator 1 includes in the inside at least one projection shape part 2a that projects to the inner side. Therefore, it is possible to rninirnize the pressure loss at the time when refrigerant gas passes through the inflow pipe 2 while fulfilling limitation of an insert position of the refrigerant piping that is connected to the main body of the air conditioner.
[0048] While the effect of the present embodiment will be described, the general hermetic type compressor 200 and the suction accumulator 21 are described first. [0049] Fig. 9 and Fig. 10 are the diagrams shown for comparison. Fig. 9 is the

longitudinal sectional view showing the overall structure of the general hermetic type compressor 200. Fig. 10 is the diagram describing a part of the suction accumulator 21 of the general hermetic type compressor 200 in section.
[0050] The general hermetic type compressor 200 shown in Fig. 9 is different only in the suction accumulator 21 from the hermetic type compressor 100 in Fig. 1. A compression element 201, an electric motor element 202, a hermetic container 210, a glass terminal 220, a discharge pipe 230, and a compression chamber suction port engaging section 24 in the hermetic type compressor 200 correspond respectively to the compression element 101, the electric motor element 102, the hermetic container 110, the glass terminal 120, the discharge pipe 130, and the compression chamber suction port engaging section 4 in the hermetic type compressor 100. [0051] The suction accumulator 21 of the general hermetic type compressor 200 is different from the suction accumulator 1 of the present embodiment in the following points.
a. An inflow pipe 22 that is provided in the suction accumulator 21 is inserted down to
an inside of a body 25. The part above an outlet of the inflow pipe 22 in the body 25 is
an ineffective volume in terms of refrigerant flow (see Fig. 10).
b. Sudden enlargement loss is extraordinary large since a refrigerant flow path from the
inflow pipe 22 to the body 25 is enlarged suddenly (the spread angle is approximately
180 degrees).
c. An outflow part 28 of an outflow pipe 23 is a straight pipe, whose diameter is not
what is reduced its size to fit the compression chamber suction port engaging section 24
of the hermetic type compressor 200. Therefore, the smooth flow of the refrigerant gas
roils at the compression chamber suction port engaging section 24 of the hermetic type
compressor 200.

d. An inflow port 27 of the outflow pipe 23 is not in a bell-mouth shape. [0052] Fig. 5 and Fig. 6 are the diagrams describing the first embodiment. Fig. 5 is the diagram describing the relation between the spread angle in the gently broadening pipe and the pressure loss. Fig. 6 is the diagram describing the relation between the diameter of the outflow pipe and the pressure loss.
[0053] As previously mentioned, the suction accumulator 1 of the present invention is different from the suction accumulator 21 of the general hermetic type compressor 200 in that the suction accumulator 1 is smoothly connected by the small spread angle (10 to 60 degrees) from the inflow pipe 2 that is provided in the suction accumulator 1 to the body 5, and the diffuser shape part 6 having the curve (for example, the circular arc) convex to the inner side. Therefore, the ineffective volume as the flow path that exists in the suction accumulator 21 of the general hermetic type compressor 200 does not exist. Since the spread angle from the inflow pipe 2 to the body 5 is small (10 to 60 degrees), the sudden enlargement loss gets extraordinary small (see Fig. 5). [0054] The inflow port 7 of the outflow pipe 3 that is provided in the suction accumulator 1 is in a circular shape or a bell-mouth shape having the diameter larger than the diameter of the inflow pipe 2. Therefore, the sudden contraction loss at the time when refrigerant gas flows in the inflow port 7 of the outflow pipe 3 and the pipe friction loss at the time when refrigerant gas passes through the inside of the outflow pipe 3 get extraordinary small, as shown in Fig. 6.
[0055] As mentioned above, in the hermetic type compressor 100 including the suction accumulator 1 or 1-1 of the present embodiment, shapes of the body 5, the inflow pipe 2 and the outflow pipe 3 of the suction accumulator 1 are selected within ranges which ensure the capacity of the body 5 that can fulfill the functions of performing gas-liquid separation of suctioned refrigerant gas, and of accumulating the separated liquid

refrigerant including the refrigerant oil. The body 5 and the inflow pipe 2 are smoothly connected by the diffuser shape part 6 with the spread angle having the diffuser effect and the curve (for example, the circular arc) convex to the inner side. In this way, the pressure loss of the refrigerant gas at the time when the refrigerant gas passes through the suction accumulator 1 is minimized. Therefore, the suction efficiency of the refrigerant gas is improved, and the pressure of the refrigerant gas that is taken in the compression chamber suction port engaging section 4 of the hermetic type compressor 100 is increased. By making the compression work be close to the ideal pressure state of the refrigeration cycle, the compressor efficiency is increased. Additionally, by improving the pressure in the evaporator that is equipped in the main body of the air conditioner, there is an effect to improve the refrigeration cycle efficiency.
Numerous additional modifications and variations are possible in light of the above teachings. It is therefore to be understood that, within the scope of the appended claims, the disclosure of this patent specification may be practiced otherwise than as specifically described herein. Reference Signs List
[0056] 1 Suction accumulator, 1-1 Suction accumulator, 2 Inflow pipe, 2a Projection shape part, 3 Outflow pipe, 3-1 Outflow pipe, 4 Compression chamber suction port engaging section, 5 Body, 6 Diffuser shape part, 7 Inflow port, 7-1 Inflow port, 8 Outflow part, 9 Ring member, 10 Oil returning hole, 21 Suction accumulator, 22 Inflow pipe, 23 Outflow pipe, 24 Compression chamber suction port engaging section, 25 Body, 27 Inflow port, 28 Outflow part, 52 Four-way valve, 53 Outdoor side heat exchanger, 54 Decompression device, 55 Indoor side heat exchanger, 56 Outdoor side blower, 57 Indoor side blower, 59 Top panel, 60 Front panel, 61 Side panel, 62 Separator, 63

Electrical item box, 64 Refrigerant piping and refrigerant circuit components, 68 Bottom plate, 100 Hermetic type compressor, 102 Electric motor element, 110 Hermetic container, 120 Glass terminal, 130 Discharge pipe, 200 Hermetic type compressor, 201 Compression element, 202 Electric motor element, 210 Hermetic container, 220 Glass terminal, 230 Discharge pipe, 300 Outdoor unit.

CLAIMS
[1 ] A hermetic type compressor comprising a suction accumulator provided at a side part of a hermetic container, the suction accumulator including:
an inflow pipe being a straight pipe with a constant inner diameter, whereto a refrigerant piping in a refrigeration cycle is connected;
a body having a cylindrical shape as a whole, whose both ends are narrowed, the body being formed with a predetermined diameter so as to have a capacity that fulfills a function of performing a gas-liquid separation of suctioned refrigerant gas, and of accumulating separated liquid refrigerant including refrigerant oil, an end part of the body on a side of the inflow pipe being formed in a diffuser shape with a predetermined spread angle, and a diffuser shape part of the body being formed smoothly in a curve convex to an inner side and being connected to the inflow pipe; and
at least one piece of an outflow pipe having an inflow port with a diameter larger than a diameter of the inflow pipe, or an inflow port with a bell-mouth shape.
[2] The hermetic type compressor according to claim 1, wherein the inflow pipe
includes inside thereof a projection shape part, the projection shape part projecting toward an inner side for deterniining a position of the refrigerant piping in the refrigeration cycle.
[3] The hermetic type compressor according to claim 1 or 2, wherein a diameter of an outflow part of the outflow pipe is reduced so as to fit a compression chamber suction port engaging section in the hermetic type compressor.

[4] The hermetic type compressor according to any one of claims 1 through 3, wherein the outflow pipe includes in a lower part inside the body an oil returning hole for returning the refrigerant oil to the hermetic type compressor.
[5] The hermetic type compressor according to any one of claims 1 through 4, wherein the predetermined spread angle is 10 to 60 degrees.