JPH11173284A - Scroll compressor - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To suppress the generation of vibration of a sealed container, to enhance the effect of low vibration and low noise of the compressor by installing a discharge muffler,
To obtain a scroll compressor with excellent vibration and noise. SOLUTION: A closed vessel 7, a fixed scroll 1, an orbiting scroll 2, a discharge muffler 8, and a discharge pipe 14 for guiding a refrigerant gas out of the closed container 7 are provided, and a position of a discharge port 8a of the discharge muffler 8 is provided. Is set so that the phase of the discharge pipe 14 mounted on the upper surface of the closed container 7 is substantially opposite to the phase of the discharge muffler 8 substantially parallel to the axial direction of the closed container 7.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for air conditioning, freezing, refrigerators, and the like.

[0002]

2. Description of the Related Art FIG.
FIG. 1 is a partial configuration diagram illustrating a rotary compressor disclosed in Japanese Patent Application Laid-Open Publication No. HEI 10-125, FIG. In the figure, reference numeral 40 denotes a cylinder fixed to the closed container 7, and a central portion is a cylindrical space. Reference numeral 41 denotes a cylindrical rolling piston having an outer shape smaller than the inner diameter of the cylindrical space of the cylinder 40;
0 in the center space. Reference numeral 42 denotes a bearing member fixed to the cylinder 40, and has a bearing 42a at the center. Reference numeral 6 denotes a main shaft for driving the rolling piston 41, which is supported by a bearing 42a of a bearing member 42. 8 is fixed to the bearing member 42 and the bearing member 4
2 is a discharge muffler for forming a muffler space 30 between the discharge vessel 2 and the discharge port 8a, and has a discharge port 8a for discharging the refrigerant gas to the high-pressure space 31 in the sealed container 7. Reference numeral 14 denotes a discharge pipe which is hermetically fixed to the closed container 7 and discharges the refrigerant gas out of the closed container 7.

Next, the operation during operation will be described. The driving torque acting on the main shaft 6 drives the rolling piston 41, and the crescent-shaped compression chamber 22 formed between the rolling piston 41 and the cylinder 40 has a similar reduction in volume to achieve a compression operation. I do. The low-pressure refrigerant gas taken into the compression chamber 22 is compressed, and the high-pressure refrigerant gas is discharged to the muffler space 30 and discharged to the high-pressure space 31 in the sealed container 7 through the discharge port 8a of the discharge muffler 8. Is discharged out of the closed container 7 through the discharge pipe 14.

A pressure wave is generated in the refrigerant gas during the compression process in the compression chamber 22, but the refrigerant gas passes through a passage whose cross-sectional area changes from the muffler space 30 to the discharge port 8a of the discharge muffler 8, whereby a specific frequency component is generated. Is attenuated to some extent. However, the discharge port 8a of the discharge muffler 8 and the discharge pipe 1
4 is located close to the high pressure space 31 from the discharge port 8a.
Most of the refrigerant gas discharged into the closed vessel 7 directly collides with the wall surface of the closed vessel 7 and enters the discharge pipe 14.
, Which generates a large force to generate vibration, which causes an increase in vibration and noise of the compressor.

[0005]

Since the conventional rotary compressor is configured as described above, even if the discharge muffler 8 is installed to attenuate the pressure wave generated in the compression chamber 22, the compressor is closed. Large vibration is generated in the container 7, and vibration of the compressor
There were problems such as an increase in noise.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and it is intended to suppress the occurrence of vibration of a closed container, to enhance the effect of low vibration and low noise of a compressor by installing a discharge muffler, An object is to obtain a scroll compressor excellent in noise.

[0007]

SUMMARY OF THE INVENTION A scroll compressor according to the present invention is formed by an airtight container and a base plate provided in the airtight container and having plate-shaped spiral teeth. A fixed scroll with a certain discharge port,
An orbiting scroll formed by a plate-shaped spiral tooth and a base plate portion forming a compression chamber between the plate-shaped spiral tooth of the fixed scroll,
A muffler space is fixed between the base plate portion of the fixed scroll and the sealed container to form a muffler space between the fixed scroll or a member fixed to the fixed scroll, and a discharge port for discharging the refrigerant gas to the high-pressure space in the closed container. A discharge muffler having an outlet, and a discharge pipe fixed to the upper portion of the closed vessel and guiding the refrigerant gas to the outside of the closed vessel, wherein the position of the discharge port is set on the surface of the discharge muffler substantially parallel to the axial direction of the closed vessel. Is set so as to have a phase substantially opposite to that of the upper part of the closed container.

Further, another discharge port is provided on the surface of the discharge muffler substantially perpendicular to the axial direction of the closed container.

Further, another discharge muffler is installed in a muffler space formed by the discharge muffler.

Further, a chamber space is formed between the base plate of the fixed scroll and the discharge muffler and between the base plate of the fixed scroll and a discharge member having a discharge valve is provided.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 Hereinafter, an example of an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows an example of an embodiment of the present invention, and is a configuration diagram of a scroll compressor. In the figure, reference numeral 1 denotes a fixed scroll, an outer peripheral portion of a base plate portion 1a is fixed to a frame 4, and an outer peripheral portion of the frame 4 is fixed to a closed container 7 by shrink fitting. A discharge port 1c is formed near the center of the base plate portion 1a of the fixed scroll 1, and the base plate portion 1a
Is formed with plate-shaped spiral teeth 1b on one side.

Reference numeral 2 denotes an orbiting scroll, on one side of a base plate portion 2a, formed are plate-shaped spiral teeth 2b having substantially the same shape as the plate-shaped spiral teeth of the fixed scroll. Swing scroll 2
A hollow cylindrical boss is formed at the center of the base plate portion 2a opposite to the plate-shaped spiral teeth 2b, and a bearing 2c is formed at the hollow cylindrical boss. Further, the outer peripheral side of the base plate portion 2a of the orbiting scroll 2 on the same side as the hollow cylindrical boss portion forms a thrust surface 2d, and is capable of sliding in a plane contact with the thrust bearing 4a of the frame 4. . Also,
Outside the thrust surface 2d of the orbiting scroll 2, a pair of 2
An Oldham guide groove 2e is formed at a location, and an upper pawl 12a of the Oldham ring 12 is engaged slidably in a linear direction.

An Oldham guide groove is also formed on the frame 4 with a phase difference of about 90.degree. From the Oldham guide groove 2e of the orbiting scroll 2, and a lower claw 12b of the Oldham ring 12 is linearly slidably engaged. ing. Frame 4
A bearing 4c for radially supporting the main shaft 6 driven by the electric motor 10 is formed at the center of the shaft.

A pin portion 6a having a plane portion in the same direction as the eccentric direction of the orbiting scroll 2 is formed at the end of the main shaft 6 on the orbiting scroll side. 6 is engaged with the pin portion 6a. The outer surface of the slider 5 has a cylindrical shape and is rotatably engaged with the bearing 2c of the orbiting scroll 2.

Further, the plate-shaped spiral teeth 1b of the fixed scroll 1
And the base plate portion 2a of the orbiting scroll 2 and the base plate portion 1a of the fixed scroll 1 and the plate-shaped spiral teeth 2 of the orbiting scroll 2
The tip of b is set so as to have a predetermined minute gap during assembly.

Reference numeral 13 denotes a suction pipe which is hermetically fixed to the closed vessel 7 and guides the low-pressure refrigerant gas before being compressed into the closed vessel 7, and 14 is hermetically fixed at an eccentric position on the upper surface of the closed vessel 7, The discharge pipe discharges the compressed high-pressure refrigerant gas to the outside of the closed container 7.

A discharge muffler 8 is fixed to a base plate portion 1a of the fixed scroll 1 opposite to the plate-shaped spiral teeth 1b.
A muffler space 30 is formed between the base plate 1a.
On the surface of the discharge muffler 8 substantially parallel to the axial direction of the closed container 7, the refrigerant gas is supplied to the high pressure space 31 in the closed container 7 at a position substantially opposite to the phase eccentric to the closed container of the discharge pipe 14.
Is provided with a discharge port 8a for discharging the liquid.

The driving torque generated by the electric motor 10 is transmitted via the main shaft 6 to the slider 5 which revolves. The driving torque transmitted to the slider 5 is
c, the orbiting scroll 2 is restrained from rotating with respect to the frame 4 and, consequently, from rotating with respect to the fixed scroll 1 by the Oldham ring 12. Perform rocking motion.

The low-pressure refrigerant gas sucked from the suction pipe 13 is formed by meshing the plate-shaped spiral teeth 1b formed on the fixed scroll 1 with the plate-shaped spiral teeth 2b formed on the orbiting scroll 2. The compression operation is realized by being taken in by a pair of crescent-shaped compression chambers 22, and the crescent-shaped compression chambers decreasing in volume in a similar manner.

Further, the compressed high-pressure refrigerant gas passes through the discharge port 1c of the fixed scroll 1 and the muffler space 3.
0, is discharged to the high-pressure space 31 through the discharge port 8a of the discharge muffler 8, passes through the discharge pipe 14, and
It is discharged outside.

Further, the flat portion of the pin portion 6a of the main shaft 6 and the flat portion of the inner surface of the slider 5 can linearly slide in the eccentric direction of the orbiting scroll 2, so that centrifugal force or the like is applied to the orbiting scroll 2. When the predetermined force acts in the eccentric direction, the orbiting scroll 2 is pressed against the fixed scroll 1 in the radial direction, and the side surface of the plate-shaped spiral tooth 2b of the orbiting scroll 2 and the plate-shaped spiral tooth 1b of the fixed scroll 1 are moved. Prevent gaps on the sides.

In the compression process of the compression chamber 22, a pressure wave is generated in the refrigerant gas, which propagates to the high-pressure space 31 and gives vibration to the closed vessel 7, which causes vibration and noise of the compressor. The pressure wave of the specific frequency component can be attenuated by passing the refrigerant gas through the passage where the pressure changes, so that the shape and length of the discharge port 1c, the discharge muffler 8, and the discharge port 8a of the fixed scroll 1 are set. By doing so, the pressure wave of the frequency component that has a large effect on the vibration and noise of the compressor is attenuated.

The upper portion of the closed container 7 has a top portion 7a directly above the shape of the shape, and the amplitude of vibration is most likely to be the largest. However, the discharge port is formed on the surface of the discharge muffler 8 substantially parallel to the axial direction of the closed container 7. Since the discharge port 8a is provided, the discharge port 8a is located away from the top portion 7a of the closed container 7, and
The pressure wave of the refrigerant gas discharged into the high-pressure space 31 through “a” does not cause a large vibration in the closed container 7.

Further, since the discharge port 8a of the discharge muffler 8 is provided at a position substantially opposite to the eccentric phase of the discharge pipe 14 with respect to the closed container 7, the discharge port 8a is
4, the refrigerant gas discharged into the high-pressure space 31 through the discharge port 8a flows along the wall surface of the sealed container 7 toward the discharge pipe 14, so that the refrigerant gas is almost closed container. 7 without directly colliding with the wall of the discharge pipe 14.
to go into. Therefore, the refrigerant gas does not apply a large force to the closed container 7 and no large vibration is generated in the closed container 7, so that the vibration and noise of the compressor are significantly reduced.

Embodiment 2 In the first embodiment described above,
Since the flow path of the refrigerant gas is complicated, the discharge flow path expands rapidly,
In some cases, the pressure loss due to rapid contraction or bending increases and the efficiency of the compressor decreases. In this case, however, the surface of the discharge muffler 8 is substantially perpendicular to the axial direction of the closed container 7 as shown in FIG. When another discharge port 8b is added, the refrigerant gas partially passes through the discharge port 8a, and the rest passes through the discharge port 8b with a small pressure loss, so that the position and the sectional area of the discharge port 8a and the discharge port 8b are determined. By setting, the reduction in compressor efficiency can be suppressed while reducing the vibration and noise of the compressor.

Embodiment 3 FIG. As shown in FIG. 3, another discharge port 32a is further provided in the muffler space 30 of the first embodiment.
Is provided, a muffler space A34 is formed between the base plate portion 1a of the fixed scroll 1 and the inner discharge muffler 32, and a muffler space B35 is formed between the inner discharge muffler 32 and the sealed container 7. Is done. Accordingly, the refrigerant gas is discharged to the muffler space A34 through the discharge port 1c of the fixed scroll 1, is discharged to the muffler space B35 through the discharge port 32a of the inner discharge muffler 32, and is discharged through the discharge port 8a of the discharge muffler 8. Since the pressure wave is discharged into the high-pressure space 31, the frequency region of the pressure wave to be attenuated by the change in the flow path cross-sectional area is expanded, and the vibration and noise of the compressor are further reduced.

Embodiment 4 A discharge valve 37 is provided to prevent the backflow of the refrigerant gas in the discharge port 1c of the fixed scroll 1.
When it is necessary to further change the flow path cross-sectional area between the discharge valve 37 and the compression chamber 22, the plate-shaped spiral tooth 1 of the fixed scroll 1 according to the first embodiment of the present invention as shown in FIG.
When the discharge member 33 having the discharge port 33a is fixed to the base plate portion 1a on the opposite side to the base plate b and the chamber space 36 is formed between the discharge member 33 and the base plate portion 1a, the refrigerant gas passes through the discharge port 1c of the fixed scroll 1 Discharged into the chamber space 36,
The muffler space 30 passes through the discharge port 33a of the discharge member 33.
And is discharged into the high-pressure space 31 through the discharge port 8a of the discharge muffler 8, so that the frequency region of the pressure wave to be attenuated by the change in the cross-sectional area of the flow path is expanded, and the vibration of the compressor having the discharge valve 37 is increased. , Noise is further reduced.

[0028]

In the scroll compressor according to the present invention, the position of the discharge port is set on the surface of the discharge muffler substantially parallel to the axial direction of the closed vessel, at a phase substantially opposite to the phase of the upper portion of the closed vessel of the discharge pipe mounted. Therefore, the discharge port is located away from the top of the closed container, and the pressure wave of the refrigerant gas discharged into the high-pressure space through the discharge port does not cause large vibration in the closed container. Is located away from the discharge pipe, and the refrigerant gas discharged into the high-pressure space through the discharge port generates a flow along the wall surface of the closed vessel toward the discharge pipe. Since the refrigerant gas does not directly impinge on the discharge pipe, the refrigerant gas does not apply a large force to the closed container, and no large vibration is generated in the closed container, so that a scroll compressor excellent in terms of vibration and noise can be obtained.

Further, since another discharge port is provided on the surface of the discharge muffler which is substantially perpendicular to the axial direction of the closed container, the refrigerant gas does not generate a large vibration in the closed container, and another discharge port having a small pressure loss. Since it passes through the outlet separately, by setting the position of each discharge port and the value of the cross-sectional area, there is an effect that a scroll compressor excellent in efficiency can be obtained while reducing vibration and noise of the compressor.

Further, since another discharge muffler is installed in the muffler space formed by the discharge muffler,
Since the frequency region of the pressure wave to be attenuated by the change in the flow path cross-sectional area is expanded, a scroll compressor excellent in vibration and noise can be obtained.

In addition, since the discharge member is arranged between the fixed scroll base plate and the discharge muffler, and a chamber space is formed between the fixed scroll base plate and the discharge member, the discharge member is attenuated by a change in the flow path cross-sectional area. Since the frequency range of the pressure wave is expanded, there is an effect that a scroll compressor excellent in vibration and noise can be obtained while having a discharge valve.

[Brief description of the drawings]

FIG. 1 is a diagram illustrating an example of an embodiment of the present invention, and is a configuration diagram of a scroll compressor.

FIG. 2 is a diagram showing another example of the embodiment of the present invention;
It is a lineblock diagram of a scroll compressor.

FIG. 3 is a diagram showing another example of the embodiment of the present invention;
It is a lineblock diagram of a scroll compressor.

FIG. 4 is a diagram showing another example of the embodiment of the present invention;
It is a lineblock diagram of a scroll compressor.

FIG. 5 is a configuration diagram of a conventional scroll compressor.

[Explanation of symbols]

Reference Signs List 1 fixed scroll, 1a base plate portion, 1b plate-shaped spiral tooth, 1c discharge port, 2 oscillating scroll, 2a base plate portion, 2b plate-shaped spiral tooth, 2c bearing, 2d thrust surface, 2e Oldham guide groove, 4 frame, 4a thrust bearing, 4b Oldham guide groove, 4c bearing, 5 slider, 6 main shaft, 6a pin portion, 7 sealed container, 8 discharge muffler, 8a discharge port, 8b discharge port B, 10 electric motor, 12 Oldham ring, 12a upper pawl, 12b
Lower nail, 13 suction pipe, 14 discharge pipe, 22 compression chamber, 3
0 muffler space, 31 high pressure space, 32 internal muffler, 32a discharge port, 33 discharge member, 33a discharge port, 34 muffler space A, 35 muffler space B, 36 chamber space, 37 discharge valve, 40 cylinder, 41 rolling piston, 42 bearing member, 4
2a Bearing.

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Kazuyuki Akiyama 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Corporation

Claims (4)

[Claims] A fixed scroll provided in the closed container, formed of a base plate portion having plate-shaped spiral teeth, and provided with a discharge port serving as a refrigerant gas passage in a central portion; An orbiting scroll formed by a plate-shaped spiral tooth and a base plate portion forming a compression chamber between the plate-shaped spiral tooth of the scroll, and fixed between the base plate portion of the fixed scroll and the closed container; Forming a muffler space between the fixed scroll or a member fixed to the fixed scroll, a discharge muffler having a discharge port for discharging refrigerant gas to a high-pressure space in the closed container, and fixed to an upper portion of the closed container; A discharge pipe for guiding the refrigerant gas to the outside of the closed container, wherein the position of the discharge port is set on the surface of the discharge muffler substantially parallel to the axial direction of the closed container. Scroll compressor according to the phase, characterized in that set to be approximately the opposite phase. 2. The scroll compressor according to claim 1, wherein another discharge port is provided on a surface of the discharge muffler substantially perpendicular to an axial direction of the closed container. 3. The scroll compressor according to claim 1, wherein another discharge muffler is installed in a muffler space formed by the discharge muffler. 4. A discharge chamber having a discharge space and a chamber space formed between the base plate portion of the fixed scroll and the discharge muffler, between the base plate portion of the fixed scroll and the discharge muffler. The scroll compressor according to claim 1, wherein