KR20220029845A - Rotary compressor - Google Patents

Abstract

According to the present invention, a rotary compressor can attenuate the entire vibration noise since a discharge passage, which communicates with a noise space of a discharge muffler with one end sealed, at a bearing is formed in a bearing plate and a discharge passage, which is connected to the discharge passage at the bearing and which guides a refrigerant discharged into the noise space of the discharge muffler, at a shaft is formed in a rotating shaft. At the same time, the rotary compressor can effectively attenuate a noise in a low frequency band since a discharge passage of the rotating shaft is formed long and narrow.

Description

Rotary Compressor

The present invention relates to a rotary compressor, and more particularly to a low-noise rotary compressor.

In general, in a rotary compressor, a roller rotates or rotates in the compression space of a cylinder, and a cylinder or a vane provided to slide on the roller is in contact with the roller or cylinder to form a compression space between the suction chamber and the compression chamber (or discharge chamber) will be separated into The compressed space compresses the refrigerant as the volume (volume) is narrowed due to the turning or rotational motion of the roller, and the compressed refrigerant is discharged toward the inner space of the casing.

Such a rotary compressor is provided with a discharge valve to open and close the discharge port. When the refrigerant in the compressed space is discharged, discharge noise and pressure pulsation are generated while opening and closing the discharge port. Accordingly, the rotary compressor is provided with a discharge muffler to attenuate discharge noise and pressure pulsation generated when refrigerant is discharged from the compression space.

The discharge muffler is installed to accommodate the discharge port. When there is only one discharge port, only one discharge muffler is installed, and when there is a plurality of discharge ports, it is common that a plurality of discharge mufflers are also installed.

For example, in a single-type rotary compressor, when the discharge port is formed only on the upper bearing, the discharge muffler is installed only on the upper bearing, whereas when the discharge port is formed on the upper bearing and the lower bearing, the upper discharge muffler is provided on the upper bearing and the lower bearing, respectively and a lower discharge muffler are installed. Since the double rotary compressor is provided with a plurality of discharge ports to discharge the refrigerant from each compression space, an upper discharge muffler and a lower discharge muffler may be installed even in the double rotary compressor.

As described above, the refrigerant discharge mechanism is similar even when only the upper discharge muffler is provided, as well as when the upper and lower discharge mufflers are provided respectively. For example, when an upper discharge muffler is provided as in the prior art (Japanese Patent Laid-Open No. 2016-102640), a discharge hole is formed in the upper surface of the discharge muffler, or the inner circumferential surface of the discharge muffler and the boss of the main bearing plate facing it A discharge gap is formed between the parts.

Then, the refrigerant discharged into the inner space of the discharge muffler is discharged to the inner space of the casing through the discharge through hole or discharge gap of the discharge muffler, and this refrigerant is discharged through the air gap between the stator and the rotor or through the through hole provided in the rotor. After moving to the upper space of the compressor, it is discharged to the outside of the compressor through a discharge pipe communicating with the upper space of the casing.

However, in the conventional rotary compressor as described above, vibration noise generated while the refrigerant is discharged from the compression chamber to the noise reducing chamber of the discharge muffler is attenuated in the noise space of the discharge muffler, which is provided in the discharge muffler There is a problem in that the above-described vibration noise cannot be sufficiently attenuated because the volume of the noise space is limited. In particular, the vibration noise of the low frequency band may still exist even if it passes through the discharge muffler, thereby aggravating the vibration noise of the compressor.

In addition, in the conventional rotary compressor, the refrigerant discharged to the noise space of the discharge muffler is discharged to the inner space of the casing after passing through the discharge muffler, and the refrigerant is discharged into the air gap between the stator and the rotor or the through hole of the rotor. As it passes through and moves to the upper space of the casing, the refrigerant forms a strong vortex in the upper space of the casing while moving with a wide rotation radius along the rotating rotor or the periphery of the rotor, thereby aggravating the discharge pulsation. Secondary vibration noise may be generated in the discharge pipe due to the discharge pulsation of the refrigerant.

Japanese Patent Laid-Open No. 2016-102640 (published date: 2016.6.2.)

It is an object of the present invention to provide a rotary compressor capable of effectively attenuating discharge noise of a refrigerant discharged from a compression chamber.

Another object of the present invention is to provide a rotary compressor capable of effectively attenuating noise in a low frequency band among discharge noise.

Another object of the present invention is to provide a rotary compressor capable of reducing the rotation radius of the discharged refrigerant to lower the discharge pulsation and thereby attenuate noise in the entire band.

In order to achieve the object of the present invention, there can be provided a rotary compressor capable of effectively attenuating noise in a low frequency band by forming a discharge passage inside the rotating shaft to increase the length and decrease the diameter of the discharge passage.

Through this, it is possible to reduce the secondary vibration noise caused by the discharge pulsation by reducing the rotation radius for the discharge path of the refrigerant discharged from the compression chamber to alleviate the eddy current of the refrigerant.

In addition, in order to achieve the object of the present invention, the inner space of the discharge muffler for accommodating the discharge port is sealed, and a discharge passage communicating with a boss portion of a bearing supporting the rotation shaft and a rotation shaft facing the same is formed, and the boss portion and the By forming an annular communication groove between the respective discharge passages of the rotating shaft, the rotary compressor can be discharged by smoothly moving the refrigerant discharged into the inner space of the discharge muffler to the discharge passage of the rotating shaft.

Furthermore, by installing the expansion muffler at the upper end of the rotating shaft, the rotational force of the refrigerant passing through the discharge passage of the rotating shaft is attenuated, thereby further reducing the secondary vibration noise caused by the discharge pulsation of the refrigerant.

In addition, in order to achieve the object of the present invention, the casing; a driving motor provided in the inner space of the casing; at least one or more cylinders provided in the inner space of the casing to form a compression chamber; a plurality of bearing plates coupled to the at least one cylinder and including a plate portion having a discharge port and a boss portion extending in an axial direction from the plate portion; a rotating shaft having one end coupled to the rotor of the driving motor and the other end coupled through the plurality of bearing plates; and at least one discharge muffler provided on at least one bearing plate of the plurality of bearing plates and provided with a noise space to be separated from the inner space of the casing, wherein the bearing plate has one end of the discharge muffler. A bearing-side discharge passage communicating with the noise space is formed, and the rotation shaft has a shaft-side discharge passage communicating with the bearing-side discharge passage and guiding the refrigerant discharged into the noise space of the discharge muffler to be discharged into the inner space of the casing. A rotary compressor may be provided.

Here, a communication groove may be formed in at least one of the inner peripheral surface of the boss part and the outer peripheral surface of the rotating shaft facing it, and the bearing-side discharge passage and the shaft-side discharge passage may communicate with each other by the communication groove.

A cross-sectional area of the communication groove may be greater than or equal to a cross-sectional area of the bearing-side discharge passage or a cross-sectional area of the shaft-side discharge passage.

In addition, a plurality of outlets of the bearing-side discharge passage are formed at predetermined intervals along the circumferential direction of the boss, and the inlet of the shaft-side discharge passage facing the outlet of the bearing-side discharge passage is in the circumferential direction of the rotation shaft. A plurality of communication grooves may be formed at a predetermined interval along the .

In addition, the outlets of the plurality of bearing-side discharge passages and the inlets of the plurality of shaft-side discharge passages may be formed to be positioned on the same line in a radial direction.

Here, an expansion muffler may be further provided at an end of the rotation shaft, and the expansion muffler may be provided to cross the longitudinal direction of the rotation shaft.

The expansion muffler may include at least one plate having a cross-sectional area greater than a cross-sectional area of the shaft-side discharge passage, and a center of the expansion muffler may be disposed to be positioned on the same line as an axial center of the shaft-side discharge passage.

The expansion muffler may include a first plate coupled to an end of the rotation shaft, a second plate spaced apart from the first plate by a predetermined distance in the axial direction with respect to the first plate, and between the first plate and the second plate. It consists of a spacer provided in the spacer, and the spacer is made up of a plurality and may be arranged at a predetermined interval along the circumferential direction.

Here, the bearing-side discharge passage may be formed to penetrate between the outer peripheral surface and the inner peripheral surface of the boss part.

In addition, the bearing-side discharge passage may be formed in a radial direction or inclined with respect to the axial direction.

Here, the shaft-side discharge passage may include a longitudinal passage formed in the longitudinal direction of the rotation shaft, and a connection direction passage passing between the outer peripheral surface of the rotation shaft and the inner peripheral surface of the longitudinal passage.

In addition, the connection direction passage may be formed in a radial direction or inclined with respect to the axial direction.

In addition, a cross-sectional area of the longitudinal passage may be larger than a cross-sectional area of the connecting passage.

Here, an oil supply hole is formed at an end supported by the bearing plate among both ends of the rotation shaft, and the oil supply hole may be formed to a position separated from the shaft-side discharge passage.

Here, the cross-sectional area of the bearing-side discharge passage may be formed to be greater than or equal to the cross-sectional area of the shaft-side discharge passage.

In addition, a cross-sectional area of the discharge port may be greater than or equal to a cross-sectional area of the bearing-side discharge passage.

In the rotary compressor according to the present invention, instead of sealing the discharge muffler, the discharge passage is formed between the boss part of the bearing included in the discharge muffler and the rotating shaft facing it and the discharge passage to extend in the axial direction to the rotating shaft, thereby creating a noise space of the discharge muffler. The discharge noise may be canceled by guiding the discharged refrigerant to the discharge passage of the rotating shaft. Through this, while attenuating the overall vibration noise of the compressor, it is possible to effectively attenuate the noise in the low frequency band as the discharge passage of the rotating shaft is long and narrow.

In addition, in the rotary compressor according to the present invention, the refrigerant discharged to the noise space of the discharge muffler is guided to the upper space of the casing by guiding the refrigerant to the discharge passage provided on the rotating shaft, so that the discharge pulsation of the refrigerant discharged to the discharge pipe is reduced 2 It can reduce car vibration noise.

In addition, in the rotary compressor according to the present invention, an expansion muffler is installed at the upper end of the rotating shaft to decrease the rotational force of the refrigerant discharged through the rotating shaft. Through this, it is possible to further reduce the secondary vibration noise by reducing the discharge pulsation generated in the upper space of the casing.

1 is a longitudinal cross-sectional view showing a rotary compressor according to the present embodiment;
2 is a perspective view showing the electric part and the compression part in the rotary compressor according to FIG.
3 is an enlarged perspective view of part "A" of FIG. 2;
FIG. 4 is a perspective view showing the breakage in FIG. 2 to explain the discharge passage of the refrigerant; FIG.
Fig. 5 is a plan view of Fig. 4;
6 is a schematic view showing the movement state of the refrigerant according to the rotation angle of the rotation shaft;
7 is a cross-sectional view showing another embodiment of the discharge passage of the refrigerant;
8 is a graph showing the noise improvement effect according to the present embodiment compared with the conventional one.

Hereinafter, a rotary compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

1 is a longitudinal cross-sectional view showing a rotary compressor according to the present embodiment.

Referring to FIG. 1 , in the rotary compressor according to the present invention, the electric part 120 is installed in the inner space 110a of the casing 110 , and the refrigerant is sucked and compressed on the lower side of the electric part 120 , and then the casing A compression unit 130 for discharging to the inner space 110a of 110 is installed. The electric part 120 and the compression part 130 are mechanically connected by a rotating shaft 125 .

The casing 110 may be installed in a longitudinal direction or may be installed in a transverse direction depending on the installation type. The installation direction is defined with respect to the rotation shaft 125 . For example, the longitudinal direction is a direction in which the rotating shaft 125 is perpendicular to the ground, and the transverse direction is a direction in which the rotating shaft 125 is installed parallel or inclined with respect to the ground. Hereinafter, a case in which the casing is provided in the longitudinal direction will be described as an example.

The inner space of the casing 110 is sealed, and the suction pipe 112 connected to the outlet side of the accumulator (not shown) is coupled to the lower half. A discharge pipe 113 connected to the condenser is coupled to the upper portion of the casing 110 . The discharge pipe 113 may be coupled on a straight line with the center of the rotation shaft 125 to be described later.

The suction pipe 112 passes through the casing 110 and is directly connected to the suction port 1331 of the cylinder 133 , and the discharge pipe 113 passes through the casing 110 and communicates with the inner space 110a. Accordingly, the compressor forms a high-pressure compressor in which the inner space 110a of the casing 110 achieves a discharge pressure.

In the electric part 120 , the stator 121 is press-fitted into the casing 110 to be fixed, and the rotor 122 is rotatably inserted into the stator 121 . A rotating shaft 125 is press-fitted to the center of the rotor 122 .

The rotating shaft 125 includes a shaft portion 1251 coupled to the rotor 122, a main bearing portion 1252 extending from the shaft portion 1251 and supported by a main bearing 131 to be described later, and a main bearing portion 1252. An eccentric portion 1253 extending from and accommodated in the compression chamber V of the cylinder 133 to be described later, and a sub-bearing portion 1254 extending from the eccentric portion 1253 and supported by a sub-bearing 132 to be described later. can be done

A shaft-side discharge passage 1255 to be described later is formed inside the shaft portion 1251 and the main bearing portion 1252 , and an oil supply passage 1257 is formed inside the eccentric portion 1253 and the sub-bearing portion 1254 . do. The shaft side discharge passage 1255 and the oil supply passage 1257 are formed separately from each other. Accordingly, the refrigerant discharged through the shaft-side discharge passage 1255 and the oil supplied through the oil supply passage 1257 are separated from each other inside the rotating shaft 125 without mixing. The shaft-side discharge passage will be described again later along with the bearing-side discharge passage.

In the compression unit 130 , a main bearing plate (hereinafter, a main bearing) 131 supporting the rotation shaft 125 is fixedly coupled to the inner circumferential surface of the casing 110 , and the main bearing 131 is located below the main bearing 131 . ) and a sub-bearing plate (hereinafter, sub-bearing) 120 for supporting the rotating shaft 125 is provided. In the longitudinal direction, the main bearing 131 may be referred to as an upper bearing, and the sub bearing 132 may be referred to as a lower bearing.

A cylinder 133 forming a compression chamber V is provided between the main bearing 131 and the sub bearing 132 together with the main bearing 131 and the sub bearing 132 . The cylinder 133 is fixed by bolting to the main bearing 131 together with the sub bearing 132 .

The compression chamber V of the cylinder 133 is provided with a rolling piston 134 coupled to the eccentric portion 1253 of the rotating shaft 125 to compress the refrigerant while performing a turning motion, and a rolling piston is formed on the inner wall of the cylinder 133 . A vane 135 that divides the compression chamber V into a suction chamber and a compression chamber together with the rolling piston 134 in contact with the 134 is slidably inserted.

The main bearing 131 covers the upper surface of the cylinder 133 and extends in the axial direction from the main plate part 1311 and the main plate part 1311 to form a compression chamber V together to support the rotation shaft 125 . and a main boss unit 1312.

The main plate portion 1311 is formed in a disk shape, and the outer circumferential surface is press-fitted or welded to the inner circumferential surface of the casing 110 to be coupled thereto. A discharge port 1313 for discharging the refrigerant compressed in the compression chamber V is formed in the main plate unit 1311, and a discharge valve 1315 for opening and closing the discharge port 1313 is installed at an end of the discharge port 1313. .

A discharge muffler 136 for accommodating the discharge valve 1315 is installed on the upper surface of the main plate 1311 . A noise space 136a separated from the inner space 110a of the casing 110 is formed inside the discharge muffler 136 .

For example, the discharge muffler 136 has a through hole 136b through which the main boss unit 1312 passes in the center thereof, and the inner peripheral surface of the through hole 136b of the discharge muffler 136 is the main boss unit 1312 . ) to be in close contact with the outer circumferential surface of Then, the noise space 136a of the discharge muffler 136 may be separated from the inner space 110a of the casing 110 and sealed.

A main shaft hole 1312a through which the rotating shaft 125 is supported is formed in the main boss portion 1312 , and a bearing-side discharge passage 1316 is formed in the middle of the main boss portion 1312 . The bearing-side discharge passage 1316 may penetrate from the outer circumferential surface of the main boss 1312 to the inner surface. The bearing-side discharge passage will be described again later along with the shaft-side discharge passage.

The sub-bearing 132 includes a sub-plate part 1321 that forms a compression chamber V together with the cylinder 133 , and a sub-boss part extending in the axial direction from the sub-plate part 1321 to support the rotating shaft 125 . (1322).

The sub-plate part 1321 is formed in a disk shape and is bolted to the main plate part 1311 together with the cylinder 133, and the sub-boss part 1322 has a sub-shaft hole 1322a through which the rotating shaft 125 is penetrated and supported. ) is formed.

The cylinder 133 is formed in an annular shape, and the compression chamber V is formed therein by the main bearing 131 and the sub bearing 132, and at one side of the cylinder 133, a suction port 1331 penetrates from the outer circumferential surface to the inner circumferential surface. ) is formed, and a vane slot 1332 into which the vane 135 is slidably inserted is formed at one side of the suction port 1331 , and a discharge guide groove 1333 is formed at one edge of the vane slot 1332 . The discharge guide groove 1333 is formed at a position communicating with the discharge port 1313 .

The rolling piston 134 is formed in an annular shape and is rotatably coupled to the eccentric portion 1253 of the rotating shaft 125, and the vane 135 is slidably inserted into the vane slot 1332 of the cylinder 133, and the rolling piston ( 134) is in contact with the outer circumferential surface. Accordingly, the compression chamber V of the cylinder 133 is separated into a suction space (unsigned) communicating with the suction port 1331 by the vane 135 and a discharge space (unsigned) communicating with the discharge port 1313 . .

In the drawings, reference numeral 1211, which is not described, denotes a winding coil.

The rotary compressor according to the present invention as described above operates as follows.

That is, when power is applied to the stator 121, the rotor 122 and the rotating shaft 125 rotate inside the stator 121 while the rolling piston 134 makes a swivel motion, and the rolling piston 134 rotates. The volume of the suction space constituting the compression chamber (V) increases according to the rotational movement of the cylinder (133), and the refrigerant is sucked into the compression chamber (V) of the cylinder (133).

The compression chamber V is divided into a suction space and a discharge space by the rolling piston 134 and the vanes 135 , and the suction space is converted into a discharge space by the turning movement of the rolling piston 134 . At this time, the refrigerant in the suction space is gradually compressed and discharged from the discharge space to the noise space 136a of the discharge muffler 136 through the discharge port 1313 provided in the main bearing 131 .

This refrigerant is supplied through the bearing-side discharge passage 1316 provided in the main boss portion 1312 of the main bearing 131 and the shaft-side discharge passage 1255 provided in the main bearing portion 1252 of the rotary shaft 125 through the casing. (110) is discharged to the inner space (110a).

At this time, the noise of the refrigerant is primarily attenuated in the discharge space of the compression chamber V, and the noise is secondarily attenuated while passing through the shaft-side discharge passage 1255 of the rotating shaft 125 . In other words, the discharge muffler 136 serves as a primary silencer, and the shaft-side discharge passage 1255 of the rotary shaft 125 functions as a secondary silencer.

Accordingly, the noise generated while the refrigerant compressed in the compression chamber V is discharged toward the inner space 110a of the casing 110 is attenuated over the second time, so that the noise attenuation effect is greatly increased, and as a result, the compressor and The vibration noise of the outdoor unit provided with the compressor can be further reduced.

FIG. 2 is a perspective view showing the electric part and the compression part in the rotary compressor according to FIG. 1 after being broken, FIG. 3 is an enlarged perspective view of part "A" of FIG. 2, and FIG. 4 is to explain the discharge passage of the refrigerant in FIG. It is a perspective view that is broken down for the purpose, and FIG. 5 is a plan view of FIG. 4 .

2 to 4 , the bearing-side discharge passage 1316 according to the present embodiment may be formed to penetrate between the outer peripheral surface and the inner peripheral surface of the main boss 1312 as described above.

For example, the inlet of the bearing-side discharge passage 1316 may be formed on the outer circumferential surface of the main boss 1312 , and may be formed at a height accommodated in the noise space 136a of the discharge muffler 136 . The outlet of the bearing-side discharge passage 1316 is formed on the inner circumferential surface of the main boss 1312 , and may be formed at the same height as the inlet of the bearing-side discharge passage 1316 .

In other words, the bearing-side discharge passage 1316 may be formed in a radial direction. Accordingly, it is possible to minimize the decompression loss of the refrigerant passing through the bearing-side discharge passage 1316 by minimizing the length of the bearing-side discharge passage 1316 .

A plurality of bearing-side discharge passages 1316 may be formed along the circumferential direction. In this case, the plurality of bearing-side discharge passages 1316 may be formed at equal intervals along the circumferential direction. Accordingly, the refrigerant filled in the noise space 136a of the discharge muffler 136 may be uniformly distributed through the bearing-side discharge passage 1316 to move to the shaft-side discharge passage 1255 .

Referring to FIG. 5 , the total cross-sectional area A2 of the discharge passage 1316 on the bearing side may be smaller than or equal to the cross-sectional area A1 of the discharge port 1313 . Accordingly, the second pressure of the refrigerant passing through the bearing-side discharge passage 1316 is slightly lower than the first pressure of the refrigerant discharged through the discharge port 1313 , and the refrigerant moves toward the bearing-side discharge passage 1316 more quickly. can

In addition, the shaft-side discharge passage 1255 is a longitudinal passage 1255a formed along the longitudinal direction of the rotation shaft 125 and a connection direction passage 1255b passing between the outer peripheral surface of the rotation shaft and the inner peripheral surface of the longitudinal passage 1255a. ) may be included.

Referring back to FIG. 1 , the longitudinal passage 1255a may be formed to be recessed by a predetermined depth along the longitudinal direction from the upper end of the rotation shaft 125 . The longitudinal passage 1255a may be formed in the axial direction or may be formed inclined with respect to the axial direction.

When the longitudinal passage 1255a is formed in the axial direction, the flow of the refrigerant passing through the longitudinal passage 1255a is linearized to reduce pulsating noise and the like in the discharge pipe 113 . On the other hand, when the longitudinal passage 1255a is formed to be inclined with respect to the axial direction, the flow rate of the refrigerant may be increased while the flow of the refrigerant is helical.

Referring to FIG. 5 , the cross-sectional area A3 of the longitudinal passage 1255a may be smaller than or equal to the total cross-sectional area A2 of the bearing-side discharge passage 1316 to be described later. For example, the cross-sectional area A3 of the longitudinal passage 1255a may be smaller than the total cross-sectional area A2 of the bearing-side discharge passage 1316 to be described later. Then, the third pressure of the refrigerant passing through the longitudinal passage 1255a is slightly lower than the second pressure of the refrigerant passing through the bearing-side discharge passage 1316, and then the noise space 136a of the discharge muffler 136 is lowered. The refrigerant discharged to the may move to the inner space (110a) of the casing (110) more quickly. In addition, the fourth pressure of the refrigerant passing through the longitudinal passage 1255a is slightly lower than the third pressure of the refrigerant discharged through the connection passage 1255b, so that the refrigerant can move to the longitudinal passage 1255a more quickly. there is.

The connection direction passage 1255b may be formed through the lower end of the longitudinal passage 1255a toward the outer circumferential surface of the rotation shaft 125 . For example, the inlet of the connection direction passage 1255b is formed on the outer peripheral surface of the rotation shaft 125, and the bearing-side discharge passage 1316 and the radially corresponding position to face the outlet of the bearing-side discharge passage 1316. can be formed in

Accordingly, the outlets of the plurality of bearing-side discharge passages 1316 and the inlets of the plurality of connection direction passages 1255b are positioned on the same line in the radial direction. Then, the outlets of the plurality of bearing-side discharge passages 1316 and the inlets of the plurality of connection direction passages 1255b communicate at the same time so that the refrigerant passing through the plurality of bearing-side discharge passages 1316 passes through the inlet of the connection direction passage 1255b. You can move more quickly towards

The connection direction passage 1255b may be formed in a radial direction like the bearing-side discharge passage 1316 . In this case, the decompression loss of the refrigerant passing through the connection direction passage 1255b can be minimized by minimizing the length of the connection direction passage 1255b.

A plurality of connection direction passages 1255b may be formed along the circumferential direction. In this case, the plurality of bearing-side discharge passages 1316 may be formed at equal intervals along the circumferential direction. Accordingly, the refrigerant filled in the noise space 136a of the discharge muffler 136 may be uniformly distributed through the bearing-side discharge passage 1316 to move to the shaft-side discharge passage 1255 .

However, the entire cross-sectional area of the connection direction passage 1255b may be smaller than the cross-sectional area of the bearing-side discharge passage 1316 or the longitudinal passage 1255a. For example, when the cross-sectional area of each connection direction passage 1255b is the same as the cross-sectional area of each bearing-side discharge passage 1316, as shown in FIG. 4, the total number of connection direction passages 1255b is the total number of the bearing-side discharge passage 1316. It may be formed smaller than the number.

Accordingly, the connection direction passage 1255b forms a neck portion of the Helmholtz resonator together with the bearing-side discharge passage 1316, and the longitudinal passage 1255a forms a volume portion of the Helmholtz resonator. will form Through this, the noise attenuation effect in the shaft-side discharge passage 1255 may be improved.

Although not shown in the drawings, the cross-sectional area at the outlet of the longitudinal passage 1255b may be smaller than the cross-sectional area at the middle of the longitudinal passage 1255b. For example, the inner diameter of the shaft hole 1261a provided in the first plate 1261 of the expansion muffler 126 to be described later may be smaller than the inner diameter of the longitudinal passage 1255b. In this case, the longitudinal passage 1255b is in a semi-sealed state, so that the noise attenuation effect can be further improved. However, even in this case, the inner diameter of the shaft hole 1261a provided in the first plate 1261 is preferably formed within a range in which the flow resistance does not increase.

Meanwhile, referring to FIGS. 2 and 3 , a communication groove 1256 may be formed in at least one of the inner peripheral surface of the main boss part 312 and the outer peripheral surface of the rotating shaft 125 facing it. The communication groove 1256 may be formed in an annular shape to accommodate the outlet of the bearing-side discharge passage 1316 or the inlet of the shaft-side discharge passage 1255, that is, the inlet of the connection direction passage 1255b.

For example, the communication groove 1256 may be formed to be stepped on the outer peripheral surface of the rotation shaft 125 . Accordingly, the outlets of the plurality of bearing-side discharge passages 1316 may communicate with the inlets of the plurality of shaft-side discharge passages 1255 through the communication groove 1256 , that is, the inlets of the connection direction passages 1255b.

A cross-sectional area of the communication groove 1256 may be greater than or equal to a cross-sectional area of the bearing-side discharge passage 1316 or a cross-sectional area of the shaft-side discharge passage 1255 . Accordingly, the refrigerant passing through the bearing-side discharge passage 1316 can quickly move to the shaft-side discharge passage 1255 .

6 is a schematic diagram showing the movement state of the refrigerant according to the rotation angle of the rotation shaft.

For example, when the outlet of the bearing-side discharge passage 1316 and the inlet of the shaft-side discharge passage 1255 are positioned on a straight line in the radial direction, as shown in Fig. 6(a), the shaft-side discharge passage ( Even if the communication groove 1256 is not formed on the inlet side of 1255 , the refrigerant can quickly flow into the shaft-side discharge passage 1255 after passing through the bearing-side discharge passage 1316 .

On the other hand, as shown in (b) of FIG. 6 , the rotation shaft 125 rotates further so that the outlet of the bearing-side discharge passage 1316 and the inlet of the shaft-side discharge passage 1255 are not positioned in a straight line in the radial direction. , the refrigerant discharged into the noise space 136a of the discharge muffler 136 may not quickly flow into the shaft side discharge passage 1255 after passing through the bearing side discharge passage 1316 . However, as the annular communication groove 1256 is formed on the inlet side of the shaft-side discharge passage 1255, the refrigerant passes through the bearing-side discharge passage 1316 and then moves along the annular communication groove 1256. Thus, it can be quickly introduced into the shaft-side discharge passage 1255 .

Meanwhile, an expansion muffler 126 may be provided at the upper end of the rotation shaft 125 .

Referring back to FIGS. 1 and 2 , the expansion muffler 126 according to the present embodiment may be disposed in a direction crossing the flow direction of the refrigerant discharged through the shaft side discharge passage 1255 of the rotation shaft 125 . .

For example, the expansion muffler 126 includes plates 1261 and 1262 that are larger than the cross-sectional area of the shaft side discharge passage 1255, and the center of the expansion muffler 126 is located in the axial direction of the shaft side discharge passage 1255. It may be arranged to be positioned on the same line with the center CL.

Specifically, the expansion muffler 126 is provided between the first plate 1261 and the second plate 1262 , and the first plate 1261 and the second plate 1262 , so that the first plate 1261 and the second plate 1262 are disposed. The second plate 1262 may be formed of a plurality of spacers 1263 spaced apart by a predetermined interval in the axial direction.

The first plate 1261 is formed in an annular shape having a shaft hole in the center. The shaft hole of the first plate 1261 is inserted into and coupled to the outer peripheral surface of the upper end of the rotation shaft. Accordingly, the shaft hole of the first plate 1261 is formed to be larger than the inner diameter of the shaft side discharge passage 1255 of the rotation shaft.

A plurality of spacer 1263 through-holes are formed at an edge of the first plate 1261 , and each spacer 1263 is inserted into and coupled to the plurality of spacer through-holes (unsigned). The plurality of spacers 1263 may pass through a spacer through hole (unsigned) of the first plate 1261 to be coupled to the rotor. Accordingly, the lower surface of the first plate 1261 may be spaced apart from the upper surface of the rotor by a predetermined distance. Then, the refrigerant discharged through the shaft-side discharge passage 1255 of the rotating shaft can be smoothly discharged without colliding with the winding coil 1211 provided in the stator 121 .

The second plate 1262 may be formed in a disk shape, and the outer diameter of the second plate 1262 may be substantially the same as the outer diameter of the first plate 1261 . Accordingly, like the first plate 1261 , the second plate 1262 may be formed to be at least larger than the outer diameter of the rotation shaft 125 .

Also, the center of the second plate 1262 may be disposed to be positioned on the same line as the axial center CL of the shaft-side discharge passage 1255 like the shaft hole 1261a of the first plate 1261 . Accordingly, the central portion of the second plate 1262 becomes a portion facing the shaft-side discharge passage 1255 of the rotation shaft 125 in the axial direction. Then, the refrigerant discharged in the axial direction through the shaft-side discharge passage 1255 of the rotating shaft 125 is blocked by the central portion of the clogged second plate 1262, so that the refrigerant flow direction is bent in the radial direction. Then, the strong rotational force of the refrigerant discharged through the shaft-side discharge passage 1255 of the rotating shaft 125 is reduced, so that the secondary vibration noise can be suppressed.

In addition, the first plate 1261 and the second plate 1262 is preferably formed of a plate material as thin and light as possible as it is coupled to the rotation shaft 125 or the rotor 122 . Accordingly, it is possible to suppress an excessive increase in the weight of the rotating body including the rotating shaft or the rotor by the expansion muffler 126 .

The plurality of spacers 1263 according to the present exemplary embodiment may be disposed between the plurality of plates 1261 and 1262 in the circumferential direction. In the plurality of spacers 1263 , a cross-sectional area (shown in FIG. 1 ) A4 formed by an interval between adjacent spacers 1263 may be formed to be larger than a cross-sectional area A3 of the shaft-side discharge passage 1255 . Accordingly, the refrigerant collided with the second plate 1262 may be bent in the lateral direction to be smoothly discharged into the inner space 110a of the casing 110 through the passage between the spacers 1263 .

On the other hand, there are other embodiments of the bearing-side discharge passage and the shaft-side discharge passage as follows.

That is, in the above-described embodiment, the bearing-side discharge passage and the shaft-side discharge passage (to be precise, the connection direction passage) are formed in the radial direction, but in some cases, the connection direction passage between the bearing-side discharge passage and the shaft-side discharge passage is inclined. may be formed.

As in the above embodiment, when the bearing-side discharge passage is formed in the radial direction, a vortex may be generated before the refrigerant passing through the bearing-side discharge passage enters the shaft-side discharge passage.

Similarly, when the connecting passage is formed in the radial direction, the connecting passage and the longitudinal passage are substantially orthogonal to each other, and then the refrigerant passing through the connecting passage can generate a vortex in the longitudinal passage.

Accordingly, in the present embodiment, the bearing-side discharge passage and/or the connection direction passage may be formed to be inclined. 7 is a cross-sectional view showing another embodiment of the discharge passage of the refrigerant.

7, the bearing-side discharge passage 1316 is inclined with respect to the axial direction, for example, the outlet of the bearing-side discharge passage 1316 may be formed higher than the inlet of the bearing-side discharge passage 1316. there is.

Accordingly, when the refrigerant that has passed through the bearing-side discharge passage 1316 enters the shaft-side discharge passage 1255 , it is possible to effectively suppress the occurrence of a vortex in the communication groove 1256 , which will be described later.

In addition, the connection direction passage 1255b is formed to be inclined with respect to the axial direction, for example, the outlet of the connection direction passage 1255b may be formed higher than the inlet of the connection direction passage 1255b.

Accordingly, it is possible to suppress the occurrence of a vortex in the refrigerant passing through the connection direction passage 1255b in the longitudinal passage 1255a so that the refrigerant is smoothly discharged.

Here, it may be preferable in terms of smooth flow of the refrigerant that the connection direction passage 1255b is inclined so as to be in line with the bearing-side discharge passage 1316 .

On the other hand, the outlet of the bearing-side discharge passage 1316 is formed at a position higher than the inlet of the bearing-side discharge passage 1316, and the outlet of the connection direction passage 1255b is formed at a position higher than the entrance of the connection direction passage 1255b. can be Accordingly, it is possible to avoid interfering with the upper end of the shaft-side discharge passage (1255), that is, the lower end of the longitudinal passage (1255a) and the oil supply passage (1257).

8 is a graph showing the noise improvement effect according to the present embodiment compared with the conventional one.

Referring to FIG. 8 , in the case of the rotary compressor equipped with the noise reduction device through the rotary shaft 125 according to the present embodiment, the noise reduction effect in all bands is higher than that of the rotary compressor using the discharge muffler 136 as in the prior art. It can be seen that there is a significant improvement.

For example, in the 50~200Hz band (S1), which is the main area of hearing loss, the noise is reduced by about 10dB, and in the 200~1600Hz band (S2), which is the main area of radiated noise from the outdoor unit, the radiated noise is reduced by about 10~30dB. , it can be seen that the outdoor unit noise is lowered by about 40dB in the 1600~2000Hz band (S3), which is the high frequency range of the outdoor unit.

It can be seen that the noise in the low frequency band is attenuated as the noise is attenuated using the relatively long and narrow shaft side discharge passage 1255 provided inside the rotation shaft 125 .

In addition, as the refrigerant is discharged through the shaft-side discharge passage 1255 of the rotating shaft 125, a eddy current that may be generated inside the casing 110 is blocked, thereby reducing the secondary vibration noise caused by the discharge pulsation. can be In addition, as the rotational force of the refrigerant discharged through the shaft-side discharge passage 1255 is attenuated by the expansion muffler 126 provided at the upper end of the rotating shaft 125, the secondary vibration noise caused by the discharge pulsation is further reduced. it can be seen that

Meanwhile, in the above-described embodiment, a single-cylinder rotary compressor has been described as an example, but in some cases, the same may be applied to a double-type rotary compressor in which a cylinder is disposed along the axial direction. Since this is the same as the above-described embodiment, a detailed description thereof is replaced with the description of the above-described embodiment.

110: casing 110a: inner space
112: suction pipe 113: discharge pipe
120: electric part 121: stator
1211: winding coil 122: rotor
125: rotation shaft 1251: shaft portion
1252: main bearing 1253: eccentric
1254: sub bearing part 1255: shaft side discharge passage
1255a: longitudinal passage 1255b: connecting passage
1256: communication home 1257: oil supply passage
126: expansion muffler 1261: first plate
1262: second plate 1263: spacer
130: compression unit 131: main bearing plate
1311: main plate unit 1312: main boss unit
1312a: main shaft hole 1313: discharge port
1315: discharge valve 1316: bearing side discharge passage
132: sub-bearing plate 1321: sub-plate portion
1322: sub-boss part 1322a: sub-shaft hole
133: cylinder 1331: intake port
1332: vane slot 1333: discharge guide home
134: rolling piston 135: vane
136: discharge muffler 136a: noise space
136b: through hole A1: cross-sectional area of the outlet
A2: Cross-sectional area of the discharge passage on the bearing side A3: Cross-sectional area of the discharge passage on the shaft side
A4: Cross-sectional area between spacers CL: Shaft center
V: compression chamber

Claims (16)

casing;
a driving motor provided in the inner space of the casing;
at least one or more cylinders provided in the inner space of the casing to form a compression chamber;
a plurality of bearing plates coupled to the at least one cylinder and including a plate portion having a discharge port and a boss portion extending in the axial direction from the plate portion;
a rotating shaft having one end coupled to the rotor of the driving motor and the other end coupled through the plurality of bearing plates; and
at least one discharge muffler provided on at least one bearing plate of the plurality of bearing plates and provided with a noise space so as to be separated from the inner space of the casing;
The bearing plate has a bearing-side discharge passage having one end communicating with the noise space of the discharge muffler,
A rotary compressor having a shaft-side discharge passage communicating with the bearing-side discharge passage and guiding the refrigerant discharged to the noise space of the discharge muffler to be discharged into the inner space of the casing in the rotation shaft. According to claim 1,
A communication groove is formed in at least one of the inner peripheral surface of the boss part and the outer peripheral surface of the rotating shaft facing it,
The bearing-side discharge passage and the shaft-side discharge passage communicate with each other through the communication groove. 3. The method of claim 2,
and a cross-sectional area of the communication groove is greater than or equal to a cross-sectional area of the bearing-side discharge passage or a cross-sectional area of the shaft-side discharge passage. 3. The method of claim 2,
A plurality of outlets of the bearing-side discharge passage are formed at predetermined intervals along the circumferential direction of the boss, and the inlet of the shaft-side discharge passage facing the outlet of the bearing-side discharge passage is in the circumferential direction of the rotation shaft. A plurality is formed at a predetermined interval,
The communication groove is formed in an annular shape to accommodate the outlets of the plurality of bearing-side discharge passages or the inlets of the plurality of shaft-side discharge passages. 5. The method of claim 4,
The rotary compressor is formed such that the outlets of the plurality of bearing-side discharge passages and the inlets of the plurality of shaft-side discharge passages are positioned on the same line in a radial direction. According to claim 1,
An expansion muffler is further provided at the end of the rotating shaft,
The expansion muffler is provided to cross the longitudinal direction of the rotation shaft. 7. The method of claim 6,
The expansion muffler includes at least one plate larger than a cross-sectional area of the shaft-side discharge passage,
The center of the expansion muffler is arranged to be positioned on the same line as the axial center of the shaft-side discharge passage. 8. The method of claim 7,
The expansion muffler is
a first plate coupled to an end of the rotation shaft;
a second plate spaced apart from the first plate by a predetermined distance in the axial direction;
Consists of a spacer provided between the first plate and the second plate,
A rotary compressor comprising a plurality of spacers and disposed at predetermined intervals along a circumferential direction. According to claim 1,
The bearing-side discharge passage is formed to pass through between the outer peripheral surface and the inner peripheral surface of the boss part. 10. The method of claim 9,
The bearing-side discharge passage is formed in a radial direction or inclined with respect to the axial direction. According to claim 1,
The shaft side discharge passage,
A rotary compressor comprising: a longitudinal passage formed in the longitudinal direction of the rotation shaft; and a connection direction passage passing between an outer peripheral surface of the rotation shaft and an inner peripheral surface of the longitudinal passage. 12. The method of claim 11,
The connecting direction passage is formed in a radial direction or inclined with respect to the axial direction. 12. The method of claim 11,
and a cross-sectional area of the longitudinal passage is larger than a cross-sectional area of the connecting passage. According to claim 1,
An oil supply hole is formed at an end supported by the bearing plate among both ends of the rotating shaft,
The oil supply hole is formed to a position where it is separated from the shaft-side discharge passage. 15. The method according to any one of claims 1 to 14,
and a cross-sectional area of the bearing-side discharge passage is greater than or equal to a cross-sectional area of the shaft-side discharge passage. 16. The method of claim 15,
A cross-sectional area of the discharge port is formed to be greater than or equal to a cross-sectional area of the discharge passage on the bearing side.

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