KR20210004170A - Scroll-type compressor - Google Patents

Abstract

The present invention relates to a compressor and, more specifically, to a scroll-type compressor capable of improving a sealing structure for sealing a compression space. According to the present invention, the scroll-type compressor includes: a casing having a sealed internal space; a motor installed in the internal case of the casing to generate rotational force, and including a stator and a rotor rotating to the stator; a rotary shaft combined with the rotor of the motor to be rotated and including an oil flow path therein; a frame installed on one side of the motor to support the rotary shaft with a gap seal and a bearing; a fixed scroll combined with the frame to form a compression space; and a rotary scroll eccentrically combined with the rotary shaft, located in the compression space, and compressing fluids by rotating with respect to the fixed scroll.

Description

Scroll-type compressor {Scroll-type compressor}

The present invention relates to a compressor, and more particularly, to a scroll type compressor capable of improving a sealing structure for sealing a compression space.

A scroll type compressor is a type of compressor capable of compressing a fluid such as a refrigerant while a fixed scroll is fixed in an inner space of a sealed casing, and a orbiting scroll is engaged with the fixed scroll to perform orbital motion.

These scroll type compressors can obtain a relatively high compression ratio compared to other types of compressors, and also have the advantage of obtaining stable torque by smoothly continuing the suction, compression and discharge processes of fluids, so they are widely used for refrigerant compression in air conditioners, etc. Is being used.

Patent Document 1 discloses a conventional scroll compressor.

Such a conventional scroll type compressor includes a housing, a fixed scroll fixed in the housing and forming a discharge chamber between the housing, and supported so as to revolve around the revolving axis in the housing, and between the fixed scroll. And an orbiting scroll for forming a compression chamber, and a shaft support member that is fixed in the housing and forms a back pressure chamber between the orbiting scroll and forms a suction chamber between the orbiting scroll.

The shaft is restrained by the main ball bearing, and the back pressure chamber and the suction part are sealed using a Teflon seal at the rear end of the main ball bearing. This structure is a structure applied to most horizontal scroll type compressors.

In such a structure, a sliding surface of the seal is generated in the rotating part of the rotating shaft, and mechanical loss occurs due to friction between the seal and the surface of the rotating shaft, and active cooling is difficult because the main ball bearing exists in the back pressure chamber.

1. Patent Publication No. 10-2011-7012574

The technical problem to be achieved by the present invention is to solve the above problems, and to provide a scroll type compressor capable of improving a sealing structure for sealing a compressed space.

In addition, the present invention is to provide a scroll type compressor capable of improving compressor performance and assembling performance by reducing mechanical friction loss by removing a sealing structure (shaft seal) of a physical rotating shaft.

In addition, the present invention is to provide a scroll type compressor capable of improving reliability by placing a bearing in a suction flow path.

In order to achieve the above technical problem, according to the present invention, first, it is possible to provide a concentric gap between the frame and the rotating shaft in order to seal the back pressure space and the suction space of the compressor. At this time, the rotating shaft may be supported by a ball bearing with respect to the frame. The concentric gap can be set larger than the gap of the ball bearing so that the gap does not physically contact even if the rotating shaft is shaken by the ball bearing.

With this configuration, the high-pressure oil enters the back pressure space through the rotation shaft, and the pressure of the back pressure space may be determined by a passage portion through which the back pressure space and the compression space communicate.

As described above, if oil is supplied to the gap seal inlet end or the gap seal through the oil flow path of the rotating shaft, leakage of gas in the back pressure chamber can be minimized, and efficiency degradation can be minimized.

As a specific example, the present invention comprises a rotating shaft coupled to the rotor of the motor and rotating and having an oil flow path therein, and a frame installed on one side of the motor and supporting the rotating shaft by a gap seal and a bearing. Can be.

As a more specific example, the present invention, in the scroll type compressor, the casing having a sealed inner space; A motor installed in the inner space of the casing to generate a rotational force and including a stator and a rotor rotating with respect to the stator; A rotating shaft coupled to the rotor of the motor to rotate and having an oil flow path therein; A frame installed on one side of the motor and supporting the rotating shaft by a gap seal and a bearing; A fixed scroll coupled to the frame to form a compression space; And an orbiting scroll that is eccentrically coupled to the rotation shaft, is located in the compression space, and compresses a fluid by performing orbiting motion with respect to the fixed scroll.

In addition, the gap seal and the bearing may be positioned adjacent to each other.

In addition, an oil flow path provided inside the rotation shaft may be connected to the gap seal.

In addition, the compressor may further include a passage through the casing, the frame, and the fixed scroll.

In addition, the oil passing through the gap seal may be supplied to the fixed scroll through the passage part.

In addition, the bearing may be a ball bearing.

In addition, a gap of the gap seal may be set larger than a gap of the ball bearing.

In addition, a first supply hole for supplying oil to the fixed scroll side may be provided in the oil passage.

In addition, a second supply hole for supplying oil to the gap seal may be provided in the oil passage.

In addition, the second supply hole may be formed inside the gap seal.

As another more specific example, the present invention, in the scroll type compressor, the casing having a sealed inner space; A motor installed in the inner space of the casing to generate a rotational force and including a stator and a rotor rotating with respect to the stator; A rotating shaft coupled to the rotor of the motor to rotate and having an oil flow path therein; A frame installed on one side of the motor, receiving oil through the oil flow path provided on the rotation shaft, and supporting the rotation shaft by gap seals and bearings installed adjacent to each other; A fixed scroll coupled to the frame to form a compression space; And an orbiting scroll that is eccentrically coupled to the rotation shaft, is located in the compression space, and compresses a fluid by performing orbiting motion with respect to the fixed scroll.

In addition, an oil flow path provided inside the rotation shaft may be connected to the gap seal.

In addition, the compressor may further include a passage through the casing, the frame, and the fixed scroll.

In addition, the fluid introduced into the casing may be introduced into a compression space between the fixed scroll and the orbiting scroll through the passage part.

In addition, the oil passing through the gap seal may be supplied to the fixed scroll through the passage part.

In addition, the gap seal may be provided at an end of the frame.

In addition, the bearing may be located inside a back pressure chamber formed by the frame inside the gap seal.

In addition, the bearing may be located outside the back pressure chamber formed by the frame.

The present invention has the following effects.

First, according to the present invention, by removing the sealing structure (shaft seal) of the physical rotating shaft, it is possible to improve compressor performance and improve assembly by reducing mechanical friction loss.

The present invention can reduce mechanical friction loss, improve assembleability, and reduce cost compared to applying a ball bearing and a shaft seal.

According to the present invention, since the axial load can be supported by the ball bearing, a separate structure is unnecessary.

In addition, the structure to which the ball bearing and the gap seal of the present invention are applied is not eccentric because the load is received from the ball bearing. Due to this, the gap remains concentric, and the amount of leakage is less than that of the eccentric gap.

In addition, as the oil passes through the gap seal, the pressure is reduced and the temperature decreases, which may help to cool the bearing. That is, since the ball bearing is located in a low-pressure part with a low temperature, there is an effect of improving reliability by cooling.

In addition, since the ball bearing is located in the low pressure portion, it is possible to prevent the ball bearing from being separated from the casing due to an increase in temperature.

Further scope of applicability of the present invention will become apparent from the detailed description below. However, since various changes and modifications within the spirit and scope of the present invention can be clearly understood by those skilled in the art, specific embodiments such as the detailed description and preferred embodiments of the present invention should be understood as being given by way of example only.

1 is a cross-sectional view showing a scroll type compressor according to a first embodiment of the present invention.
2 is a cross-sectional view showing a scroll type compressor according to a second embodiment of the present invention.
3 is a partially enlarged cross-sectional view showing an example of an oil flow path formed according to a second embodiment of the present invention.
4 is a partially enlarged cross-sectional view showing another example of an oil flow path formed according to a second embodiment of the present invention.
5 is a cross-sectional view showing a scroll type compressor according to a third embodiment of the present invention.
6 to 8 are graphs showing performance improvement according to an embodiment of the present invention.
6 shows a difference in power consumption when a gap seal according to an embodiment of the present invention is applied.
7 shows a difference in cooling power when a gap seal according to an embodiment of the present invention is applied.
8 shows the difference in performance index when a gap seal according to an embodiment of the present invention is applied.

Hereinafter, exemplary embodiments disclosed in the present specification will be described in detail with reference to the accompanying drawings, but identical or similar elements are denoted by the same reference numerals regardless of reference numerals, and redundant descriptions thereof will be omitted. The suffixes "module" and "unit" for components used in the following description are given or used interchangeably in consideration of only the ease of preparation of the specification, and do not have meanings or roles that are distinguished from each other by themselves. In addition, in describing the embodiments disclosed in the present specification, when it is determined that a detailed description of related known technologies may obscure the subject matter of the embodiments disclosed in the present specification, the detailed description thereof will be omitted. In addition, the accompanying drawings are for easy understanding of the embodiments disclosed in the present specification, and the technical idea disclosed in the present specification is not limited by the accompanying drawings, and all modifications included in the spirit and scope of the present invention It should be understood to include equivalents or substitutes.

Terms including ordinal numbers, such as first and second, may be used to describe various elements, but the elements are not limited by the terms. These terms are used only for the purpose of distinguishing one component from another component.

When a component is referred to as being "connected" or "connected" to another component, it is understood that it may be directly connected or connected to the other component, but other components may exist in the middle. Should be. On the other hand, when a component is referred to as being "directly connected" or "directly connected" to another component, it should be understood that there is no other component in the middle.

Singular expressions include plural expressions unless the context clearly indicates otherwise.

In the present application, terms such as "comprises" or "have" are intended to designate the presence of features, numbers, steps, actions, components, parts, or combinations thereof described in the specification, but one or more other features. It is to be understood that the presence or addition of elements or numbers, steps, actions, components, parts, or combinations thereof, does not preclude in advance.

1 is a cross-sectional view showing a scroll type compressor according to a first embodiment of the present invention. 1 shows a horizontal scroll type compressor.

The horizontal scroll type compressor 100 includes a casing (housing) 110 having a sealed internal space, and components for compressing fluid may be installed in the casing 110. That is, in the casing 110, a motor 200, a rotating shaft 300, a fixed scroll 500 and a revolving scroll 600 engaged with each other, and a frame 400 in which the rotating shaft 300 is installed may be included. .

The casing 110 for forming a closed space may be formed in a horizontal cylinder shape. The casing 110 may be provided with a suction port 111 and a discharge port 112 for entering and exiting the refrigerant.

A motor 200 for generating a rotational force may be installed in the inner space of the casing 110. In addition, a rotation shaft 300 coupled to the rotor 210 of the motor 200 may be installed.

The rotation shaft 300 may be eccentrically coupled to the orbiting scroll 600. That is, the motor 200 may provide rotational force through which the orbiting scroll 600 may orbit through the rotation shaft 300.

A frame 400 may be installed on one side of the motor 200. This frame 400 may be formed of a material having high hardness as a main frame.

This frame 400 may provide a support structure in which the fixed scroll 500 and the orbiting scroll 600 can be installed. That is, the fixed scroll 500 may be coupled to the frame 400 to form a compressed space 501.

At this time, the casing 110 includes a discharge chamber 101 in which refrigerant gas is discharged from the compressed space 501, and the discharge port 112 is provided in the discharge chamber 101, and the refrigerant in the discharge chamber 101 May be discharged through the discharge port 112.

In the discharge chamber 101, the oil can be separated from the refrigerant through an oil separator (not shown), and at this time, the oil separated on the lower side is stored in the oil storage unit 130, and is sucked through the oil pickup and rotated. It can be supplied to each part.

A separate inverter space may be provided on the side of the suction port 111 of the casing 110, and an inverter unit (not shown) may be located in the inverter space.

The motor 200 is installed in the inner space of the casing 110 to generate rotational force, and a stator including a stator 220 on which a winding is installed and an insulator 230 coupled to the stator 220 to insulate the winding It may include an assembly and a rotor 210 that is coupled to the stator assembly and rotates.

Meanwhile, a sealing structure for sealing the compression space may be installed at one side of the frame 400 while fixing the rotation shaft 300 so as to be rotatable.

Referring to FIG. 1, the rotation shaft 300 may be supported by a gap seal 320 and a bearing 310. That is, the sealing structure for sealing the compression space while rotatably fixing the rotation shaft 300 may include a gap seal 320 and a bearing 310.

At this time, as shown in FIG. 1, the bearing 310 may be a ball bearing. Also, the gap of the gap seal 320 may be set to be larger than the gap of the ball bearing 310.

That is, the gap seal 320 may be installed to allow oil to pass between the gap and the rotation shaft 300, and the ball bearing 310 may also be installed on the rotation shaft 300 with a predetermined gap. At this time, the gap between the gap seal 320 is set larger than the gap of the ball bearing 310 so that even if the rotation shaft is shaken by the ball bearing 310, the gap between the rotation shaft 300 of the gap seal 320 does not physically contact. Configurable.

In this way, the gap seal 320 and the bearing 310 may be positioned adjacent to each other.

Referring to FIG. 1, an oil flow path 301 formed by a hollow portion may be formed inside the rotation shaft 300, for example. The oil flow path 301 formed inside the rotation shaft 300 may be connected to the oil storage unit 130, so that the oil stored in the oil storage unit 130 may be connected to the oil flow path 301. In addition, the oil flow path 301 formed in the rotation shaft 300 may be connected to the gap seal 320.

A first supply hole 304 for supplying oil to the fixed scroll 500 may be provided in the oil passage 301. In this way, the oil supplied through the first supply hole 304 may be delivered to the discharge chamber 101 through the fixed scroll 500. In this case, the oil delivered to the discharge chamber 101 may move to the oil storage unit 130 through the process as described above.

As such, the oil supplied through the first supply hole 304 may be delivered to the sealing structure. That is, the oil supplied through the first supply hole 304 may be delivered to the bearing 310 and the gap seal 320 (path A).

The oil delivered to the bearing 310 and the gap seal 320 through the path A may be transferred to the discharge chamber 101 through the fixed scroll 500 again (path B). In this case, the oil delivered to the discharge chamber 101 may move to the oil storage unit 130 through the process as described above.

At this time, referring to FIG. 1, a passage portion 113 passing through the casing 110, the frame 400, and the fixed scroll 500 may be formed. Therefore, the oil delivered to the bearing 310 and the gap seal 320 through the A path is delivered to the discharge chamber 101 through the passage part 113, that is, through the fixed scroll 500 through the B path. Can be.

Referring to FIG. 1, it can be seen that a fluid (for example, a refrigerant) flowing into the casing 110 through the suction port 111 also flows into the fixed scroll 500 through the passage part 113. That is, the refrigerant flowing into the casing 110 through the inlet 111 may be introduced into the compression space 501 formed between the fixed scroll 500 and the orbiting scroll 600.

The gap seal 320 may be provided at the end of the frame 400. That is, the gap seal 320 may be formed through the sealing portion 410 formed at the end of the frame 400.

At this time, the bearing 310 installed together with the gap seal 320 may be located inside the back pressure chamber 401 formed inside the gap seal 320 in the frame 400 structure.

A sealing structure including the gap seal 320 and the bearing 310 will be described later in detail.

Meanwhile, between the fixed scroll 500 and the frame 400, an orbiting scroll 600 that is coupled to the fixed scroll 500 and performs orbiting motion with respect to the fixed scroll 500 may be installed.

The orbiting scroll 600 is connected to the rotation shaft 300 and is eccentrically coupled to the center of the rotation shaft 300 to implement a orbiting motion.

In this way, in the scroll type compressor 100, the compression chamber 501 is formed between the orbiting scroll 600 and the fixed scroll 500, and the back pressure chamber is between the orbiting scroll 600 and the frame 400 ( 401) can be formed.

A balance weight 700 may be installed in the back pressure chamber 401 to offset centrifugal force generated by the orbiting of the orbiting scroll 600. The balance weight 700 may be installed on the rotation shaft 300 and may be installed on a side opposite to the eccentric direction of the rotation shaft 300. In this case, a bearing 311 may be installed between the balance weight 700 and the orbiting scroll 600.

2 is a cross-sectional view showing a scroll type compressor according to a second embodiment of the present invention.

This horizontal scroll type compressor 100 includes a casing 110 having a sealed internal space, and components for compressing fluid may be installed in the casing 110. That is, in the casing 110, a motor 200, a rotating shaft 300, a fixed scroll 500 and a revolving scroll 600 engaged with each other, and a frame 400 in which the rotating shaft 300 is installed may be included. .

Hereinafter, a difference from FIG. 1 and a sealing structure will be described in detail with reference to FIG. 2.

Referring to FIG. 2, a sealing structure for sealing a compression space may be installed on one side of the frame 400 while fixing the rotation shaft 300 so as to be rotatable.

A sealing structure for sealing the compression space while rotatably fixing the rotation shaft 300 may include a gap seal 320 and a bearing 310. That is, the rotation shaft 300 may be supported by the gap seal 320 and the bearing 310.

In this case, as shown in FIG. 2, the bearing 310 may be a ball bearing. Also, the gap of the gap seal 320 may be set to be larger than the gap of the ball bearing 310.

That is, the gap seal 320 may be installed to allow oil to pass between the gap and the rotation shaft 300, and the ball bearing 310 may also be installed on the rotation shaft 300 with a predetermined gap. At this time, the gap between the gap seal 320 is set larger than the gap of the ball bearing 310 so that even if the rotation shaft is shaken by the ball bearing 310, the gap between the rotation shaft 300 of the gap seal 320 does not physically contact. Configurable.

Referring to FIG. 2, an oil flow path 301 formed by a hollow portion may be formed inside the rotation shaft 300, for example. The oil flow path 301 formed inside the rotation shaft 300 may be connected to the oil storage unit 130, so that the oil stored in the oil storage unit 130 may be connected to the oil flow path 301.

A first supply hole 304 for supplying oil to the fixed scroll 500 may be provided in the oil passage 301. In this way, the oil supplied through the first supply hole 304 may be transferred to the discharge chamber 101 after flowing into the compression space 401 through the fixed scroll 500 (path A').

In addition, a second supply hole 302 for supplying oil to the gap seal 320 may be provided in the oil passage 301. The second supply hole 302 may be formed to be directly connected to the gap seal 320 (C path). Accordingly, the oil introduced through the oil passage 301 may be transmitted to the bearing 310 and the gap seal 320 through the second supply hole 302.

In this way, the oil delivered to the bearing 310 and the gap seal 320 through the second supply hole 302 may be transferred to the discharge chamber 101 through the fixed scroll 500 again. In this case, the oil delivered to the discharge chamber 101 may move to the oil storage unit 130 through the process as described above.

In this case, referring to FIG. 2, a passage portion 113 passing through the casing 110, the frame 400, and the fixed scroll 500 may be formed. Accordingly, the oil delivered to the bearing 310 and the gap seal 320 through the C path may be delivered to the discharge chamber 101 through the fixed scroll 500 through the passage part 113.

Referring to FIG. 2, it can be seen that a fluid (for example, a refrigerant) introduced into the casing 110 through the suction port 111 also flows into the fixed scroll 500 through the passage part 113. That is, the refrigerant flowing into the casing 110 through the suction port 111 may be introduced into the compression space 501 formed between the fixed scroll 500 and the orbiting scroll 600.

The gap seal 320 may be provided at the end of the frame 400. That is, the gap seal 320 may be formed through the sealing portion 410 formed at the end of the frame 400.

At this time, the bearing 310 installed together with the gap seal 320 may be located inside the back pressure chamber 401 formed inside the gap seal 320 in the frame 400 structure.

3 is a partially enlarged cross-sectional view showing an example of an oil flow path formed according to the second embodiment of the present invention, and FIG. 4 is a partially enlarged cross-sectional view showing another example of an oil flow path formed by the second embodiment of the present invention. .

Hereinafter, an example of an oil path (oil flow path) made according to a second embodiment of the present invention will be described with reference to FIGS. 3 and 4.

As described above, the oil passage 301 may be provided with a second supply hole 302 for supplying oil to the gap seal 320. The second supply hole 302 may be formed to be directly connected to the gap seal 320.

In this case, the second supply hole 302 may be located at the inlet side of the gap seal 320. That is, as shown in FIG. 3, the second supply hole 302 may be located at the entrance side of the sealing portion 410 of the frame 400 for forming the gap seal 320.

The second supply hole 302 may be located between the bearing 310 and the gap seal 320.

Referring to FIG. 3, oil supplied through the oil flow path 301 of the rotation shaft 300 is not substantially transmitted to the bearing 310 through the second supply hole 302 but may flow into the gap seal 320. have.

Meanwhile, referring to FIG. 4, in the oil passage 301, a second supply hole 302 for supplying oil to the gap seal 320 may be positioned to be biased toward the gap seal 320. That is, the second supply hole 302 may be located in the middle of the sealing part 410 of the frame 400 forming the gap seal 320.

In other words, the second supply hole 302 may be located inside the gap seal 320. That is, the oil supplied through the second supply hole 302 may be first filled in the gap of the gap seal 320.

Referring to FIG. 4, oil supplied through the oil passage 301 of the rotation shaft 300 may first flow into the gap seal 320 through the second supply hole 302. In this case, the oil introduced into the gap seal 320 may branch to the bearing 310 side and the frame 400 outside and proceed.

That is, the oil flowing into the gap seal 320 through the second supply hole 302 may be supplied to the bearing 310 and discharged in a direction opposite to the bearing 310.

At this time, since the oil flowing into the gap seal 320 is also transferred to the bearing 310, the oil may fill the gap of the ball bearing 310. Accordingly, the fluid (refrigerant) cannot pass through the bearing 310, and a phenomenon in which the refrigerant gas inside the back pressure chamber flows back toward the frame 400 can be prevented.

5 is a cross-sectional view showing a scroll type compressor according to a third embodiment of the present invention.

This horizontal scroll type compressor 100 includes a casing 110 having a sealed internal space, and components for compressing fluid may be installed in the casing 110. That is, in the casing 110, a motor 200, a rotating shaft 300, a fixed scroll 500 and a revolving scroll 600 engaged with each other, and a frame 400 in which the rotating shaft 300 is installed may be included. .

Hereinafter, a difference from FIGS. 1 and 2 and a sealing structure will be described in detail with reference to FIG. 5.

Referring to FIG. 5, a sealing structure for sealing a compression space may be installed on one side of the frame 400 while fixing the rotation shaft 300 so as to be rotatable.

Meanwhile, a sealing structure for sealing the compression space may be installed at one side of the frame 400 while fixing the rotation shaft 300 so as to be rotatable.

Referring to FIG. 5, the rotation shaft 300 may be supported by a gap seal 321 and a bearing 311 provided adjacent to each other. That is, the sealing structure for sealing the compression space while rotatably fixing the rotation shaft 300 may include a gap seal 321 and a bearing 311.

At this time, as shown, the bearing 311 may be located outside the back pressure chamber 401 formed by the frame 400. That is, the gap seal 321 may be located between the back pressure chamber 401 and the bearing 311. In this way, the gap seal 321 may be formed by the sealing portion 411 positioned between the back pressure chamber 401 and the bearing 311.

As shown in FIG. 5, the bearing 311 may be a ball bearing. Further, the gap of the gap seal 321 may be set larger than the gap of the ball bearing 311.

That is, the gap seal 321 may be installed to allow oil to pass between the gap and the rotation shaft 300, and the ball bearing 311 may also be installed on the rotation shaft 300 with a predetermined gap. At this time, the gap of the gap seal 321 is set larger than the gap of the ball bearing 311, so that even if the rotation shaft is shaken by the ball bearing 311, the gap between the rotation shaft 300 of the gap seal 321 does not physically contact. Configurable.

Referring to FIG. 5, an oil flow path 301 formed by a hollow portion may be formed inside the rotation shaft 300, for example. The oil flow path 301 formed inside the rotation shaft 300 may be connected to the oil storage unit 130, so that the oil stored in the oil storage unit 130 may be connected to the oil flow path 301. In addition, the oil flow path 301 formed in the rotation shaft 300 may be connected to the gap seal 320.

A first supply hole 304 for supplying oil to the fixed scroll 500 may be provided in the oil passage 301. In this way, the oil supplied through the first supply hole 304 may be delivered to the discharge chamber 101 through the fixed scroll 500. In this case, the oil delivered to the discharge chamber 101 may move to the oil storage unit 130 through the process described above.

As such, the oil supplied through the first supply hole 304 may be delivered to the sealing structure. That is, the oil supplied through the first supply hole 304 may be delivered to the gap seal 321 and the bearing 311 (path A).

The oil delivered to the gap seal 321 and the bearing 311 through the path A may be transferred to the discharge chamber 101 through the fixed scroll 500 again (path B). In this case, the oil delivered to the discharge chamber 101 may move to the oil storage unit 130 through the process as described above.

In this case, referring to FIG. 5, a passage portion 113 passing through the casing 110, the frame 400, and the fixed scroll 500 may be formed. Therefore, the oil delivered to the gap seal 321 and the bearing 311 through the A path is delivered to the discharge chamber 101 through the passage part 113, that is, through the fixed scroll 500 through the B path. Can be.

That is, the oil path may be the same as in the first embodiment described with reference to FIG. 1.

Referring to FIG. 5, it can be seen that a fluid (for example, a refrigerant) flowing into the casing 110 through the suction port 111 also flows into the fixed scroll 500 through the passage part 113. That is, the refrigerant flowing into the casing 110 through the inlet 111 may be introduced into the compression space 501 formed between the fixed scroll 500 and the orbiting scroll 600.

The present invention as described above can reduce mechanical friction loss by removing the sealing structure (shaft seal) of the physical rotating shaft, thereby improving compressor performance and improving assembly.

The high-pressure oil flows into the back pressure chamber 401 through the rotation shaft 300, and the pressure in the back pressure chamber 401 is determined by a communication hole between the back pressure chamber 401 and the compression space 501. At this time, some oil leaks into the concentric gap due to the pressure difference between the back pressure chamber 401 and the suction part, and at this time, the leaked oil passes through the ball bearing 310 and bearing lubrication is performed.

If oil is supplied to the inlet end of the gap seal 320 or inside the gap seal 320 through the hollow hole-shaped oil flow path 301 of the rotary shaft 300, leakage of gas in the back pressure chamber 401 can be minimized. It is possible to minimize the decrease in efficiency.

The present invention can reduce mechanical friction loss, improve assembleability, and reduce cost compared to applying a ball bearing and a shaft seal.

The journal bearing application structure requires a separate structure for receiving an axial load. According to the present invention, since the axial load can be supported by the ball bearing 310, a separate structure is unnecessary.

In addition, in the journal bearing structure, the gap is eccentric to one side by the bearing load, whereas the structure to which the ball bearing 310 and the gap seal 320 of the present invention are applied receives a load from the ball bearing and thus does not become eccentric. Due to this, the gap remains concentric and the amount of leakage is less than that of the eccentric gap.

On the other hand, according to the present invention, since the bearing is located in the suction passage, it is possible to improve reliability.

That is, the ball bearing 310 may be located at the rear end of the concentric gap around the rotation shaft 300 so that the ball bearing 310 may be located in the suction space.

At this time, as the oil passes through the gap seal 320, the pressure is reduced and the temperature is lowered, thereby helping cooling the bearing. That is, since the ball bearing 310 is located in a low-pressure portion having a low temperature, there is an effect of improving reliability by cooling.

In addition, since the ball bearing 310 is located in the low pressure portion, it is possible to prevent the ball bearing 310 from being separated from the casing 110 due to an increase in temperature (generally, the thermal expansion of the casing 110 is larger). .

6 to 8 are graphs showing performance improvement according to an embodiment of the present invention. Specifically, FIG. 6 shows the difference in power consumption when a gap seal according to an embodiment of the present invention is applied. 7 shows a difference in cooling power when a gap seal according to an embodiment of the present invention is applied. In addition, FIG. 8 shows the difference in performance index when the gap seal according to the embodiment of the present invention is applied.

Hereinafter, an effect of applying a gap seal according to an embodiment of the present invention will be described with reference to FIGS. 6 to 8.

Referring to FIG. 6, the input means the amount of power consumed by the compressor. As shown in the figure, when a gap seal is used, the input reduction effect is higher than when a gap seal is not used (no gap seal is used).

This may be a phenomenon caused by reducing the loss due to friction occurring in the gap seal. Since the friction loss is proportional to the square of the rotational speed, the loss increases as the speed increases. Therefore, it can be seen that the effect increases as the speed increases.

Referring to FIG. 7, cooling power represents a value obtained by converting a cooling load (cold air) from a compressor into Watts.

Since the compressor uses a sealing structure instead of mechanical sealing, leakage of refrigerant may be inevitable. At this time, as the amount of the leaked refrigerant gas increases, the cooling power decreases. However, since the leakage generated by the gap seal according to the present invention is constant, it can be seen that the ratio of the leakage amount decreases as the speed increases. This means that the total amount of refrigerant circulation is proportional to the rotational speed of the compressor, but the amount of leakage is constant, and thus the ratio of the amount of leakage decreases.

Therefore, the cooling power may be reduced at low speed, but there is an effect of reducing the input at high speed.

Referring to FIG. 8, a coefficient of performance (COP) represents a value obtained by dividing a cooling power by an input. This is the case for cooling. In the case of heating operation, COP corresponds to 1+ cooling power/input. This COP may be an index to check the performance of the compressor or air conditioner.

In this way, the performance of the compressor is determined by cooling power/input, and as a result of applying the present invention and evaluating, it can be seen that the effect of reducing the input is greater than that of reducing the cooling power. In particular, it can be seen that the effect of increasing the performance at high speed is large.

Features, structures, effects, and the like described in the above embodiments are included in at least one embodiment of the present invention, and are not necessarily limited to only one embodiment. Furthermore, the features, structures, effects, and the like illustrated in each embodiment can be implemented by combining or modifying other embodiments by a person having ordinary knowledge in the field to which the embodiments belong. Accordingly, contents related to such combinations and modifications should be interpreted as being included in the scope of the present invention.

In addition, although the embodiments have been described above, these are only examples and do not limit the present invention, and those of ordinary skill in the field to which the present invention belongs are illustrated above within the scope not departing from the essential characteristics of the present embodiment. It will be seen that various modifications and applications that are not available are possible. For example, each component specifically shown in the embodiment can be modified and implemented. And differences related to these modifications and applications should be construed as being included in the scope of the present invention defined in the appended claims.

100: compressor 110: casing
200: motor 210: rotor
220: stator 230: insulator
300: rotary shaft 310, 311: ball bearing
320, 321: gap seal 400: frame
500: fixed scroll 600: orbiting scroll
700: balance weight

Claims (18)

In the scroll type compressor,
A casing having a sealed inner space;
A motor installed in the inner space of the casing to generate a rotational force and including a stator and a rotor rotating with respect to the stator;
A rotating shaft coupled to the rotor of the motor to rotate and having an oil flow path therein;
A frame installed on one side of the motor and supporting the rotating shaft by a gap seal and a bearing;
A fixed scroll coupled to the frame to form a compression space; And
And a orbiting scroll eccentrically coupled to the rotating shaft, located in the compression space, and compressing a fluid by performing orbiting motion with respect to the fixed scroll. The scroll type compressor of claim 1, wherein the clearance seal and the bearing are positioned adjacent to each other. The scroll type compressor of claim 1, wherein an oil flow path provided in the rotation shaft is connected to the gap seal. The scroll type compressor of claim 3, further comprising a passage through the casing, the frame, and the fixed scroll. The scroll type compressor of claim 4, wherein the oil passing through the gap seal is supplied to the fixed scroll side through the passage part. The scroll type compressor according to claim 1, wherein the bearing is a ball bearing. The scroll type compressor according to claim 6, wherein a gap of the gap seal is set larger than a gap of the ball bearing. The scroll type compressor of claim 1, wherein the oil passage is provided with a first supply hole for supplying oil to the fixed scroll side. The scroll type compressor of claim 8, wherein a second supply hole for supplying oil to the gap seal is provided in the oil passage. The scroll type compressor of claim 9, wherein the second supply hole is formed inside the gap seal. In the scroll type compressor,
A casing having a sealed inner space;
A motor installed in the inner space of the casing to generate a rotational force and including a stator and a rotor rotating with respect to the stator;
A rotating shaft coupled to the rotor of the motor to rotate and having an oil flow path therein;
A frame installed on one side of the motor to receive oil through the oil flow path provided on the rotation shaft and to support the rotation shaft by gap seals and bearings installed adjacent to each other;
A fixed scroll coupled to the frame to form a compression space; And
And a orbiting scroll eccentrically coupled to the rotating shaft, located in the compression space, and compressing a fluid by performing orbiting motion with respect to the fixed scroll. The scroll type compressor as claimed in claim 11, wherein an oil flow path provided inside the rotation shaft is connected to the gap seal. The scroll type compressor of claim 11, further comprising a passage through the casing, the frame, and the fixed scroll. The scroll type compressor of claim 13, wherein the fluid flowing into the casing flows into a compression space between the fixed scroll and the orbiting scroll through the passage part. The scroll type compressor of claim 13, wherein the oil passing through the gap seal is supplied to the fixed scroll side through the passage part. The scroll compressor of claim 11, wherein the gap seal is provided at an end of the frame. The scroll type compressor of claim 16, wherein the bearing is located inside a back pressure chamber formed by the frame inside the gap seal. The scroll type compressor of claim 11, wherein the bearing is located outside a back pressure chamber formed by the frame.

Images