KR102653975B1 - Rotary compressor - Google Patents

Abstract

The present invention relates to rotary compressors.
A rotary compressor according to one aspect includes a shell forming an internal space; a drive motor disposed in the inner space of the shell; and a compression mechanism unit that receives power from the drive motor and operates to compress the refrigerant, wherein the compression mechanism unit includes: a cylinder forming a chamber for compressing the refrigerant; a rotating shaft connected to the driving motor; A roller located in the chamber, connected to the rotating shaft and rotating to compress the refrigerant in the chamber; Vane slot provided in the cylinder; a vane that reciprocates along the vane slot and divides the chamber into a suction chamber and a compression chamber; and an oil supply passage formed in the cylinder to supply oil flowing along the shell to the vane slot.

Description

Rotary compressor

The present invention relates to rotary compressors.

In general, a compressor is a mechanical device that receives power from a power generator such as an electric motor or turbine and compresses air, refrigerant, or various other working gases to increase pressure, and is used in home appliances such as refrigerators and air conditioners or in industrial applications. It is widely used throughout.

These compressors can be roughly divided into reciprocating compressors, rotary compressors, and scroll compressors.

The reciprocating compressor is a compressor that forms a compression space between a piston and a cylinder into which working gas is sucked in and discharged, and compresses the refrigerant while the piston moves in a straight line inside the cylinder.

The rotary compressor is a compressor in which a compression space through which working gas is sucked in and discharged is formed between an eccentrically rotating roller and a cylinder, and the roller rotates eccentrically along the inner wall of the cylinder to compress the refrigerant.

The scroll compressor is a compressor in which a compression space through which working gas is absorbed and discharged is formed between an orbiting scroll and a fixed scroll, and the orbiting scroll rotates along the fixed scroll to compress the refrigerant.

Meanwhile, a prior document, Korea Patent Publication No. 10-2009-0012854 (published on February 4, 2009), discloses a rotary two-stage compressor.

The rotary two-stage compressor disclosed in the prior literature includes an airtight container, a low-pressure compression assembly, an intermediate plate, a high-pressure compression assembly, and an electric motor.

And, a high pressure compression assembly, an intermediate plate, and a low pressure compression assembly are sequentially arranged below the electric motor.

And, the high-pressure compression assembly includes a high-pressure cylinder, a high-pressure eccentric portion, and a high-pressure vane provided in the high-pressure cylinder. The high-pressure cylinder is provided with a vane hole in which the high-pressure vane is accommodated.

The low-pressure compression assembly includes a low-pressure cylinder, a low-pressure eccentric portion, and a low-pressure vane provided in the low-pressure cylinder. The low-pressure cylinder is provided with a vane hole in which the low-pressure vane is accommodated.

The high pressure vane and the low pressure vane reciprocate within each vane hole. Each vane hole includes a vane receiving portion that accommodates the vane, and a spring receiving portion that accommodates a spring supporting each vane and has a larger diameter than the vane hole.

And, the high-pressure eccentric part and the low-pressure eccentric part are connected to a rotating shaft, and the rotating shaft is connected to an electric motor.

Meanwhile, within the sealed container, oil fills up to the upper surface of the high pressure compression assembly. That is, the upper cylinder and the lower cylinder are submerged in the oil. In this state, oil can be supplied to the vane receiving portion through the spring receiving portion of each cylinder.

Additionally, oil rises along the oil passage formed inside the rotating shaft, and some of the oil is supplied into the upper and lower cylinders.

Additionally, a portion of the oil may flow upward along the rotating shaft, rise after being discharged from the rotating shaft, and be discharged outside the compressor through the discharge pipe along with the refrigerant.

Additionally, some of the oil may flow downward along the inner peripheral surface of the sealed container.

However, according to the prior literature, when the rotation shaft rotates at the beginning of operation of the compressor, the oil level becomes lower than the lower side of the high pressure cylinder, so oil is not supplied to the vane receiving part of the high pressure cylinder.

Therefore, there is a problem that noise due to friction between the high pressure vane and the upper cylinder increases during the reciprocating motion of the high pressure vane in the vane receiving portion.

The purpose of the present invention is to provide a rotary compressor in which oil can be smoothly supplied to the upper vane even when the oil level is low.

Additionally, the purpose of the present invention is to provide a rotary compressor that can smoothly supply oil to the upper vane even during high-speed operation.

Additionally, an object of the present invention is to provide a rotary compressor in which the recovery rate of oil flowing with the refrigerant is increased.

The rotary compressor of the present invention forms an oil supply passage for supplying oil to the vane slot in the upper cylinder where the refrigerant is compressed by the upper roller, so that even if the oil level is low, the oil flowing along the shell flows into the vane slot. It can be supplied smoothly.

In addition, the rotary compressor of the present invention allows oil flowing down the shell to be stably supplied to the vane slot by having a plurality of oil supply passages communicate with the vane slot.

Additionally, in the rotary compressor of the present invention, the oil supply passage may be composed of a first oil passage and a second oil passage. The bottom surface of the first oil passage is inclined downward toward the second oil passage, and the depth of the second oil passage is formed to be deeper than the depth of the first oil passage, so that the vane slot is formed along the oil supply passage. can be supplied smoothly.

In addition, in the rotary compressor of the present invention, when the oil supply passage passes through the bearing located on the upper side of the upper cylinder and communicates with the vane slot, oil can be smoothly supplied to the vane slot, and the oil recovery rate can be increased. You can.

According to the proposed invention, as the oil supply passage is formed in the upper cylinder, the oil flowing down the shell is supplied to the vane slot along the oil supply passage even if the oil level is low. Accordingly, friction noise from the vanes reciprocating along the vane slot can be prevented from occurring.

In addition, as the oil supply passage is formed in the upper cylinder, even when the rotary compressor operates at high speed, the oil flowing down the shell is supplied to the vane slot along the oil supply passage, enabling lubrication of the friction surface of the vane.

Additionally, when the oil supply passage passes through the bearing located on the upper side of the upper cylinder and then communicates with the vane slot, the oil recovery rate can be increased.

1 is a cross-sectional view showing the configuration of a rotary compressor according to a first embodiment of the present invention.
Figure 2 is a perspective view of the compression mechanism according to the first embodiment of the present invention.
Figure 3 is an exploded perspective view of the compression mechanism according to the first embodiment of the present invention.
Figure 4 is a view of the upper cylinder in the compression mechanism according to the first embodiment of the present invention viewed from above.
Figure 5 is a cross-sectional view taken along AA of the compression mechanism in Figure 4.
Figure 6 is a cross-sectional view of the compression mechanism in Figure 5 cut along BB. .
Figure 7 is a diagram showing oil flow within the shell according to the first embodiment of the present invention.
Figure 8 is a view showing oil flowing toward the upper vane along the oil supply passage in the upper cylinder according to the first embodiment of the present invention.
Figure 9 is a graph showing the noise level at each operating speed according to the presence or absence of an oil supply passage according to the first embodiment of the present invention.
Figure 10 is a graph showing the noise level by operating frequency according to the presence or absence of an oil supply passage according to the first embodiment of the present invention.
Figure 11 is a view of the main bearing of the compression mechanism according to the second embodiment of the present invention as seen from above.
FIG. 12 is a cross-sectional view of the compression mechanism section taken along CC in FIG. 11, and FIG. 13 is a cross-sectional view of the compression mechanism section taken along DD in FIG. 11.

Hereinafter, the rotary compressor of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a cross-sectional view showing the configuration of a rotary compressor according to a first embodiment of the present invention, FIG. 2 is a perspective view of a compression mechanism according to a first embodiment of the present invention, and FIG. 3 is a diagram showing the configuration of a rotary compressor according to a first embodiment of the present invention. This is an exploded perspective view of the compression mechanism.

1 to 3, the rotary compressor 1 according to the first embodiment of the present invention includes a shell 10 forming an internal space, and an upper cap coupled to the upper side of the shell 10. (11) and a lower cap 12 coupled to the lower side of the shell 10.

For example, the shell 10 may be formed in a cylindrical shape. Additionally, the shell 10 may include an upper opening and a lower opening.

A portion of the upper cap 11 is formed in a cylindrical shape and can be inserted into the interior of the shell 10 through an upper opening of the shell 10.

A portion of the lower cap 12 is formed in a cylindrical shape and can be inserted into the interior of the shell 10 through a lower opening of the shell 10.

Alternatively, in the present invention, the shell 10 may be open on the upper or lower side, but the other side may be closed. In this case, a single cap can cover the opening of the shell 10.

A suction pipe 13 may be connected to the shell 10, and a discharge pipe 14 may be connected to the upper cap 11.

The rotary compressor 1 may further include a drive motor 20 installed inside the shell 10, and a compression mechanism unit 30 connected to the drive motor 20 and compressing the refrigerant.

The driving motor 20 may include a stator 21 that generates magnetic force by applied power, and a rotor 22 located inside the stator 21.

The stator 21 may be fixed to the inner peripheral surface of the shell 10. However, a portion of the stator 21 may be spaced apart from the inner peripheral surface of the shell 10 so that oil can move up and down inside the shell 10 through the stator 21.

The rotor 22 may be rotated by induced electromotive force generated through interaction with the stator 21 while located within the stator 21 .

The compression mechanism unit 30 can compress the refrigerant by receiving the rotational force of the rotor 22. The compression mechanism unit 30 may be configured to compress the refrigerant in a single chamber, or may be configured to compress the refrigerant in a plurality of chambers.

FIG. 1 shows an example of a compression mechanism 30 capable of performing compression in two chambers.

The compression mechanism unit 30 may include a rotation shaft 32 that is connected to the rotor 22 and transmits rotational force.

The rotation axis 32 may extend in the vertical direction within the shell 10. An oil passage 322 for oil to flow is formed within the rotating shaft 32. The oil passage 322 is formed to penetrate the rotation shaft 32 vertically.

In addition, although not shown, a branch flow path for supplying oil to the chamber of each cylinder, which will be described later, may be branched from the oil flow path 322 on the rotation shaft 32.

The compression mechanism unit 30 may include an upper compression unit and a lower compression unit.

The upper compression unit and the lower compression unit may each be connected to the rotation shaft 32.

The upper compression unit may include an upper cylinder 42 forming an upper chamber 420 and an upper roller 35 located in the upper chamber 420 and connected to the rotation shaft 32.

The upper roller 35 is eccentrically coupled to the rotation shaft 32 and can rotate with a constant eccentric trajectory according to the rotation of the rotation shaft 32.

The upper cylinder 42 may be provided with a first vane slot 422, and the upper vane 43 may be accommodated in the first vane slot 422.

A first spring slot 423a in which an upper spring (not shown) is accommodated may be formed at an end of the first vane slot 422. The first spring slot 423a may extend from the side of the upper cylinder 42 toward the first vane slot 422.

The upper cylinder 42 may be provided with a first oil supply slot 423 through which oil flows. The first oil supply slot 423 may penetrate the upper cylinder 42 vertically.

To allow oil to flow smoothly into the first oil supply slot 423, the diameter of the first oil supply slot 423 may be formed to be larger than the width of the first vane slot 422.

Additionally, a portion of the first vane slot 422 may move to the first oil supply slot 423 during the reciprocating motion.

The first oil supply slot 423 may penetrate the first spring slot 423a vertically. Accordingly, the first spring slot 423a and the first oil supply slot 423 may intersect.

And, the first oil supply slot 423 may communicate with the first vane slot 422. Accordingly, oil flowing into the first oil supply slot 423 can be supplied to the first vane slot 422.

The upper vane 43 reciprocates within the first vane slot 422 and divides the upper chamber 420 into a suction chamber and a compression chamber.

An upper refrigerant inlet 421 through which refrigerant flows is formed in the upper cylinder 42.

The upper refrigerant inlet 421 is not limited, but may extend obliquely from the lower surface of the upper cylinder 42 toward the upper chamber 420.

Additionally, the upper cylinder 42 may further include an upper refrigerant discharge port 429 through which compressed refrigerant is discharged.

The upper compression unit may further include a main bearing (52) placed on the upper side of the upper cylinder (42).

The main bearing 52 is fixed to the inner peripheral surface of the shell 10 and covers the upper side of the upper chamber 420. The main bearing 52 may be located below and spaced apart from the drive motor 20.

The rotating shaft 32 passes through the main bearing 52 and is connected to the rotor 22. The main bearing 52 guides the rotation of the rotating shaft 32 so that it rotates stably without being eccentric.

A discharge port (see 521 in FIG. 5) communicating with the upper refrigerant discharge port 429 may be formed in the main bearing 52. An upper muffler 62 may be mounted on the main bearing 52.

The upper muffler 62 can reduce noise generated when the refrigerant compressed in the upper cylinder 42 is discharged.

The rotation shaft 32 may pass through the upper muffler 62. The upper muffler 62 may be formed with one or more passage holes 620 for the refrigerant to pass through.

The lower compression unit may include a lower cylinder 46 forming a lower chamber 460 and a lower roller 37 located in the lower chamber 460 and connected to the rotating shaft 32.

The lower roller 37 is eccentrically coupled to the rotation shaft 32 and can rotate with a constant eccentric trajectory according to the rotation of the rotation shaft 32.

The lower cylinder 46 may be provided with a second vane slot 462, and the lower vane 47 may be accommodated in the second vane slot 462.

A second spring slot 463a may be formed at an end of the second vane slot 462 to accommodate a lower spring (not shown). The second spring slot 463a may extend from the side of the lower cylinder 46 toward the second vane slot 462.

The lower cylinder 46 may be provided with a second oil supply slot 463 through which oil flows. The second oil supply slot 463 may penetrate the lower cylinder 46 up and down.

At this time, the second oil supply slot 463 may penetrate the second spring slot 463a vertically. Accordingly, the second spring slot 463a and the second oil supply slot 463 may intersect.

And the second oil supply slot 463 may communicate with the second vane slot 462. Accordingly, oil flowing into the second oil supply slot 463 can be supplied to the second vane slot 462.

The lower vane 47 reciprocates within the second vane slot 462 and divides the lower chamber 460 into a suction chamber and a compression chamber.

A lower refrigerant inlet 461 through which refrigerant flows is formed in the lower cylinder 46.

The lower refrigerant inlet 461 is not limited, but may extend obliquely from the upper surface of the lower cylinder 46 toward the lower chamber 460.

Additionally, the lower cylinder 46 may further include a lower refrigerant discharge port (not shown) through which compressed refrigerant is discharged.

The lower compression unit may further include a sub bearing (54) located below the lower cylinder (46).

The sub bearing 54 may support the lower cylinder 46. And, the sub bearing 54 may cover the lower side of the lower chamber 460.

The rotation shaft 32 may pass through the sub-bearing 54. Accordingly, the sub-bearing 54 guides the rotation of the rotating shaft 32 so that it rotates stably without being eccentric.

The sub-bearing 54 is provided with a discharge port (not shown) through which the refrigerant discharged through the lower refrigerant discharge port passes.

A lower muffler 64 may be coupled to the sub bearing 54. The lower muffler 64 can reduce noise generated when the refrigerant compressed in the lower cylinder 46 is discharged.

An oil opening 640 may be formed in the central portion of the lower muffler 64 for oil to pass through. The oil passage 322 of the rotating shaft 32 may communicate with the oil opening 640. Accordingly, the oil stored in the shell 10 can be supplied to the oil passage 322 of the rotating shaft 32 through the oil opening 640.

The compression mechanism unit 30 may further include an intermediate plate 50 positioned between the upper cylinder 42 and the lower cylinder 46.

The middle plate 50 may cover the lower side of the upper chamber 420 and the upper side of the lower chamber 460. The intermediate plate 50 prevents direct friction between the upper roller 35 and the lower roller 37 during the rotation of the rotating shaft 32.

The intermediate plate 50 may include a branch portion 502 that branches off the refrigerant sucked through the suction pipe 13. The branch portion 502 may communicate with the upper refrigerant inlet 421 and the lower refrigerant inlet 461.

And, the rotation axis 32 is arranged to penetrate the intermediate plate 50.

Meanwhile, the refrigerant compressed in the lower chamber 460 is discharged into the inner space of the lower muffler 64 through the lower refrigerant discharge port.

In addition, the refrigerant discharged into the inner space of the lower muffler 64 passes through the sub bearing 54, the lower cylinder 46, the intermediate plate 50, the upper cylinder 42, and the main bearing 52. It flows into the inner space of the upper muffler (62).

To this end, the sub-bearing 54, lower cylinder 46, intermediate plate 50, upper cylinder 42, and main bearing 52 each have refrigerant passage openings 542, 464, 506 for passage of refrigerant, 428, 522) may be provided.

Meanwhile, when the rotary compressor 1 is operated, oil flowing along the oil passage 322 during the rotation of the rotary shaft 32 is supplied to the upper chamber 420 and the lower chamber 460. Lubrication is provided on the friction surfaces of each roller (35, 37).

On the other hand, the oil stored inside the shell 10 is supplied to each vane slot (422, 462) through each oil supply slot (423, 463) to reduce friction between the upper vane (43) and the lower vane (46). It acts as a lubricant on the surface.

In general, the shell 10 must be filled with oil so that at least the upper cylinder 42 of the compression mechanism 30 is submerged in the oil.

This is because oil must be supplied to the first oil supply slot 423 of the upper cylinder 42. Therefore, it is preferable that the oil level within the shell 10 is maintained higher than the height of the upper cylinder 42.

However, when the rotary shaft 32 is initially rotating or the rotary compressor 1 is operating at high speed, the oil level in the shell 10 may become lower than the lowest point of the upper cylinder 42. You can.

In this case, oil is not supplied to the first oil supply slot 423, and the friction surface of the upper vane 43 is not lubricated, resulting in friction between the upper vane 43 and the upper cylinder 42. There is a problem of noise caused by .

Of course, even if the oil level decreases, the oil level can be maintained higher than that of the lower cylinder 46, so the problem of oil not being supplied to the lower vane 47 does not occur.

Therefore, even if the oil level in the shell 10 is low, the upper cylinder 42 of the present invention is configured to supply oil to the first vane slot 422 where the upper vane 43 is accommodated. A supply flow path 424 may be further included.

The oil supply passage 424 supplies oil that flows down along the inner peripheral surface of the shell 10 or oil that falls from within the shell 10 onto the upper surface of the upper cylinder 42 to the first vane slot 422. do.

Therefore, a portion of the upper cylinder 42 must contact the inner peripheral surface of the shell 10.

To this end, the upper cylinder 42 may include a chamber body 42a forming the upper chamber 420 and an extension portion 42b extending radially from the chamber body 42a.

The diameter of the chamber body 42a may be smaller than the inner diameter of the shell 10 and may be spaced apart from the inner peripheral surface of the shell 10.

A portion of the oil supply passage 424 may be formed in the extension portion 42b, and the other portion may be formed in the chamber body 42a.

Additionally, the first vane slot 422 extends in the radial direction from the inner peripheral surface of the chamber body 42a, and a portion of the first vane slot 422 may be located in the extension portion 42b.

At this time, the outer end of the first vane slot 422 may be spaced apart from the contact surface 42c in contact with the shell 10 in the extension portion 42b.

Additionally, the first oil supply slot 423 and the first spring slot 423a may be located in the extension portion 42b.

FIG. 4 is a view of the upper cylinder in the compression mechanism according to the first embodiment of the present invention, FIG. 5 is a cross-sectional view taken along A-A of the compression mechanism in FIG. 4, and FIG. 6 is a view of the compression mechanism in FIG. 5. This is a cross-sectional view cut along B-B.

Referring to FIGS. 4 and 5, the oil supply passage 424 includes a first oil passage 425 formed on the upper surface of the upper cylinder 42, and a downward direction from the end of the first oil passage 425. It may include a second oil passage 426 extending to.

The first oil passage 425 may be formed by being depressed downward from the upper surface of the upper cylinder 42 to a predetermined depth.

The second oil passage 426 may be formed by being depressed downward from the end of the first oil passage 425 to a predetermined depth. Additionally, the second oil flow path 426 may communicate with the first vane slot 422.

At this time, the depression depth of the second oil passage 426 may be formed deeper than the depression depth of the first oil passage 425.

To guide the oil flowing along the inner peripheral surface of the shell 10 to the first vane slot 422, the first oil flow path 425 is positioned at the contact surface 42c of the extension portion 42b. 1 It may extend toward the vane slot 422.

At this time, the first oil passage 425 is connected to the contact surface 42c of the extension portion 42b so that the friction area of the upper vane 43 in contact with the oil supplied from the first oil passage 425 is increased. It may extend across the extension portion 42b to a point on the chamber body 42a.

Also, the second oil passage 426 may be depressed downward at one point of the chamber body 42a.

For example, the second oil passage 426 may be spaced apart from the inner peripheral surface of the upper cylinder 42 and the first oil supply slot 423.

Additionally, the main bearing 52 may cover the entire upper portion of the second oil passage 426 and a portion of the first oil passage 425.

Although not limited, the distance from the second oil passage 426 to the inner peripheral surface of the upper cylinder 42 may be designed to be smaller than the distance from the second oil passage 426 to the first oil supply slot 423. You can.

In the present invention, the depression depth D1 of the second oil passage 426 is adjusted to increase the contact area between the oil supplied to the second oil passage 426 and the upper vane 43. ) or may be formed to be larger than 1/2 of the height H1 of the first oil supply slot 423.

Additionally, in the present invention, a plurality of first oil passages 425 may be provided in the upper cylinder 42 to increase the amount of oil guided by the first oil passages 425.

That is, the first oil supply slot 423 and the first vane slot 422 may be located between the two first oil passages 425.

As an example, one or more first oil passages 425 may be located on one side of the first vane slot 422, and one or more first oil passages 425 may be located on the other side of the first vane slot 422. can be located

Additionally, a plurality of second oil passages 426 may be provided in the upper cylinder 42. That is, the first vane slot 422 may be located between the two second oil passages 426.

Hereinafter, the process of compressing the refrigerant by the compression mechanism will be described.

When power is applied to the stator 21 of the driving motor 20, the rotor 22 rotates. When the rotor 22 rotates, the rotation shaft 32 rotates together.

When the rotation shaft 32 rotates, the upper roller 35 rotates eccentrically within the upper cylinder 42 and the lower roller 37 rotates eccentrically within the lower cylinder 46.

The refrigerant introduced into the shell 10 through the suction pipe 13 flows to the branch portion 502 of the middle plate 50.

Some of the refrigerant flowing into the branch 502 is introduced into the upper chamber 420 through the upper refrigerant inlet 421 of the upper cylinder 42. And, another part of the refrigerant flowing into the branch portion 502 is introduced into the lower chamber 460 through the lower refrigerant inlet 461 of the lower cylinder 46.

The refrigerant introduced into the upper chamber 420 within the upper cylinder 42 is compressed during the rotation of the upper roller 35 and then discharged from the upper chamber 420 through the upper refrigerant discharge port 429.

The refrigerant discharged from the upper chamber 420 passes through the discharge port 521 of the main bearing 52 and flows into the inner space of the upper muffler 62.

Meanwhile, the refrigerant introduced into the lower chamber 460 within the lower cylinder 46 is compressed during the rotation of the lower roller 37 and then discharged from the lower chamber 460 through the lower refrigerant discharge port.

The refrigerant discharged from the lower chamber 460 passes through the discharge port of the sub-bearing 54 and flows into the inner space of the lower muffler 64.

The refrigerant flowing into the inner space of the lower muffler 64 sequentially flows into the sub-bearing 54, lower cylinder 46, intermediate plate 50, upper cylinder 42, and main bearing 52. The refrigerant passes through openings 542, 464, 506, 428, and 522. Afterwards, the refrigerant flows into the inner space of the upper muffler 62.

The refrigerant flowing into the inner space of the upper muffler 62 is discharged from the upper muffler 62 through the passage hole 620 of the upper muffler 62.

The refrigerant discharged from the upper muffler 62 rises, passes through the drive motor 20, and is then discharged to the outside of the rotary compressor 1 through the discharge pipe 14.

Figure 7 is a diagram showing oil flow within the shell according to the first embodiment of the present invention, and Figure 8 is a diagram showing oil flowing toward the upper vane along the oil supply passage in the upper cylinder according to the first embodiment of the present invention. This is a drawing showing this.

Referring to FIGS. 1 to 8 , as described above, oil flowing along the oil passage 322 of the rotation shaft 32 may be supplied to the upper chamber 420 and the lower chamber 460.

The oil supplied to the upper chamber 420 and the lower chamber 460 performs a lubricating action during the rotation of the upper roller 35 and the lower roller 37 and then flows with the compressed refrigerant. .

Therefore, the refrigerant passing through the upper muffler 62 contains oil, and the oil along with the refrigerant can pass through the drive motor 20.

And, as shown in FIG. 7, part of the oil above the drive motor 20 may be discharged to the outside through the discharge pipe 14 together with the refrigerant, and the other part may be separated from the refrigerant and discharged into the shell ( 10) It can flow downward along the inner circumferential surface.

Additionally, oil rising along the oil passage 322 of the rotation shaft 32 may be discharged upward from the driving motor 20.

A portion of the oil discharged upward from the drive motor 20 may be discharged to the outside through the discharge pipe 14 together with the refrigerant, and the other portion may flow downward along the inner peripheral surface of the shell 10. there is.

Meanwhile, when the oil level within the shell 10 is located higher than the upper cylinder 42, oil flows into each vane slot 422 and 462 through each oil supply slot 423 and 463. can be supplied.

In this case, oil can be directly supplied to the first vane slot 422 through the oil supply passage 424.

Therefore, the lubrication of the friction surface of each vane (43, 47) is smoothed by the oil supplied to each vane slot (422, 462), thereby preventing frictional noise during the reciprocating movement of each vane (43, 47). It can be.

On the other hand, when the oil level within the shell 10 becomes lower than that of the upper cylinder 42, oil is not supplied to the first oil supply slot 423.

However, even when the oil level is lowered, some of the oil flowing along the shell 10 may be directly supplied to the first vane slot 422 through the oil supply passage 424.

At this time, so that the oil introduced into the first oil passage 425 flows stably into the second oil passage 426, the bottom of the first oil passage 425 moves toward the second oil passage 426. It may be formed to be inclined downward.

Therefore, according to the present invention, the friction surface of the upper vane 43 can be lubricated even when the oil level is lowered, and friction noise can be prevented during the reciprocating movement of the upper vane 43.

In addition, according to the oil supply passage 424 of the present invention, there is an advantage in that oil can be stably supplied to the first vane slot 422 even when the rotary compressor 1 operates at high speed.

Figure 9 is a graph showing the noise level at operating speed according to the presence or absence of an oil supply flow path according to the first embodiment of the present invention, and Figure 10 is a graph showing the operating frequency according to the presence or absence of an oil supply flow path according to the first embodiment of the present invention. This is a graph showing the noise level of each star.

9 and 10 have the same other conditions, but the only difference is the presence or absence of an oil supply passage.

First, referring to FIG. 9, it can be seen that the noise level is reduced by approximately 3 dBA for each frequency in the case where the oil supply passage is present as in the present invention compared to the case in which the oil supply passage does not exist.

In addition, referring to FIG. 10, it can be seen that when the rotary compressor is operating at high speed of 100 rps, the noise level is reduced in the frequency band of approximately 2 to 5 kHz compared to the case where the oil supply passage does not exist. You can.

Figure 11 is a view from above of the main bearing of the compression mechanism according to the second embodiment of the present invention, Figure 12 is a cross-sectional view taken along C-C of the compression mechanism in Figure 11, and Figure 13 is a view of the compression mechanism in Figure 11. This is a cross-sectional view cut along D-D.

This embodiment is the same as the first embodiment in other respects, but there is a difference in the location and shape of the oil supply passage. Therefore, hereinafter, only the characteristic parts of this embodiment will be described.

11 to 14, the oil supply flow path according to this embodiment includes a first oil flow path 526 provided in the main bearing 52, and a second oil flow path provided in the upper cylinder 42 ( 427) may be included.

Specifically, the main bearing 52 is formed with a discharge port 524 through which the refrigerant compressed in the upper cylinder 42 passes. And, the discharge port 524 is opened and closed by the discharge valve 53.

And, the first oil flow path 526 is formed adjacent to the discharge port 524. The first oil passage 526 may penetrate the main bearing 52 vertically.

An upper muffler 62 is installed above the main bearing 52, and the upper muffler 62 covers the discharge port 524 and the first oil passage 526.

The second oil passage 427 is formed by recessing downward from the upper surface of the upper cylinder 42. The second oil passage 427 communicates with the first vane slot 422 in which the upper vane 43 is accommodated.

In the present invention, the depth, location, and relative arrangement of the second oil passage 427 with surrounding components are the same as those described in the first embodiment, and therefore detailed description will be omitted.

In the present invention, the first oil passage 526 and the second oil passage 427 are aligned vertically. Accordingly, the oil in the first oil passage 526 may flow downward and enter the second oil passage 427.

In the present invention, a plurality of first oil passages 526 are provided in the main bearing 52 so that oil is smoothly supplied to the first vane slot 422, and a plurality of second oil passages are provided in the upper cylinder 42. A flow path 427 may be provided.

In this case, the first vane slot 422 may be located between the two second oil passages 427.

In this embodiment, when the oil level within the shell 10 is located higher than the upper cylinder 42, oil flows into each vane through each oil supply slot (see 423 and 463 in FIG. 3). It may be supplied to slots 422 and 462.

Even in this case, part of the oil contained in the refrigerant compressed and discharged from the upper cylinder 42 may be separated from the refrigerant in the upper muffler 62 and flow down along the inner surface of the upper muffler 62.

Additionally, the oil inside the upper muffler 62 may flow along the first oil passage 526 and the second oil passage 427 and be directly supplied to the first vane slot 422.

On the other hand, even when the oil level in the shell 10 becomes lower than the upper cylinder 42, the oil separated from the refrigerant in the upper muffler 62 flows into the first oil passage 526 and the second oil passage 526. 2 It may flow along the oil passage 427 and be directly supplied to the first vane slot 422.

Therefore, according to the present invention, the friction surface of the upper vane 43 can be lubricated even when the oil level is lowered, and friction noise can be prevented during the reciprocating movement of the upper vane 43.

In addition, there is an advantage in that oil can be stably supplied to the first vane slot 422 even when the rotary compressor 1 operates at high speed.

In particular, in the case of the present invention, the oil in the upper muffler 62 can be supplied directly to the first vane slot 422, so the amount of oil discharged to the outside of the rotary compressor 1 can be reduced.

That is, according to the present invention, there is an advantage that the oil recovery rate is increased.

In the above embodiment, the compression mechanism unit 30 includes a plurality of chambers as an example, but unlike this, even if the compression mechanism unit 30 includes one chamber, the oil supply flow path of the present invention can be used to Oil can be smoothly supplied through the vane slot.

In this case, the lower bearing and the intermediate plate are omitted from the compression mechanism unit 30, and the refrigerant can be compressed using a single cylinder and roller.

For example, oil may be supplied to the vane slot by forming a first oil passage and a second oil passage in a single cylinder as in the first embodiment.

Alternatively, as in the second embodiment, a first oil passage may be formed in the main bearing, and a second oil passage may be formed in the cylinder to supply oil to the vane slot.

1: rotary compressor 10: shell
20: Drive motor 30: Compression mechanism part
32: rotating shaft 35: upper roller
37: lower roller 42: upper cylinder
46: lower cylinder 52: main bearing
54: Sub-bearing 424: Oil supply flow path

Claims (14)

A shell forming an internal space;
a drive motor disposed in the inner space of the shell; and
It includes a compression mechanism that receives power from the drive motor and operates to compress the refrigerant,
The compression mechanism unit includes a cylinder forming a chamber for compressing refrigerant;
a rotating shaft connected to the driving motor;
A roller located in the chamber, connected to the rotating shaft and rotating to compress the refrigerant in the chamber;
Vane slot provided in the cylinder;
a vane that reciprocates along the vane slot and divides the chamber into a suction chamber and a compression chamber; and
It is formed in the cylinder and includes an oil supply passage for supplying oil flowing along the shell to the vane slot,
The oil supply passage includes a first oil passage formed by being recessed in the upper surface of the cylinder and extending toward the vane slot at a contact surface in contact with the inner peripheral surface of the shell;
A second oil flow path is formed by recessing downward from an end of the first oil flow path and communicates with the vane slot,
The cylinder includes a chamber body that forms the chamber and is spaced apart from the shell,
It includes an extension extending from the chamber body to a contact surface in contact with the shell,
The first oil flow path extends from a contact surface of the extension toward the first vane slot and across the extension to a point on the chamber body. delete According to claim 1,
A rotary compressor, characterized in that the depth of the second oil passage is deeper than the depth of the first oil passage. According to claim 1,
A rotary compressor wherein the bottom of the first oil passage slopes downward toward the second oil passage. According to claim 1,
A rotary compressor wherein the depth of the second oil passage is formed to be greater than 1/2 of the height of the vane. delete delete delete delete According to claim 1,
A rotary compressor wherein the cylinder is formed to communicate with the vane slot and is further provided with an oil supply slot for supplying oil to the vane slot. According to claim 10,
A rotary compressor, characterized in that the distance from the second oil passage to the inner peripheral surface of the cylinder is shorter than the distance from the second oil passage to the oil supply slot. According to claim 1,
A plurality of oil supply passages are provided in the cylinder,
A rotary compressor in which the vane slot is located between the plurality of oil supply passages. A shell forming an internal space;
a drive motor disposed in the inner space of the shell;
a rotating shaft connected to the driving motor;
an upper roller and a lower roller rotated by the rotating shaft;
an upper cylinder accommodating the upper roller and forming an upper chamber for compressing refrigerant;
a lower cylinder accommodating the lower roller and forming a lower chamber for compressing refrigerant;
a vane slot provided in the upper cylinder;
an upper vane that reciprocates along the vane slot and divides the upper chamber into a suction chamber and a compression chamber;
It is formed in the upper cylinder and includes an oil supply passage for supplying refrigerant flowing along the shell to the vane slot,
The oil supply passage includes a first oil passage formed by being recessed in the upper surface of the upper cylinder and extending toward the vane slot at a contact surface in contact with the inner peripheral surface of the shell;
A second oil flow path is formed by recessing downward from an end of the first oil flow path and communicates with the vane slot,
The upper cylinder includes a chamber body that forms the chamber and is spaced apart from the shell,
It includes an extension extending from the chamber body to a contact surface in contact with the shell,
The first oil flow path extends from a contact surface of the extension toward the first vane slot and across the extension to a point on the chamber body. delete

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