WO2024025159A1

WO2024025159A1 - Scroll compressor

Info

Publication number: WO2024025159A1
Application number: PCT/KR2023/008782
Authority: WO
Inventors: 이재하; 안성용; 김태경; 최세헌
Original assignee: 엘지전자 주식회사
Priority date: 2022-07-29
Filing date: 2023-06-23
Publication date: 2024-02-01
Also published as: KR20240017262A

Abstract

The present invention provides a scroll compressor comprising: a casing; a driving motor provided inside the casing; a rotation shaft rotatably coupled to the driving motor and including a first and a second eccentric portion formed to be spaced apart from each other; a first compression unit including a first orbiting scroll coupled to the first eccentric portion to enable rotation of the first orbiting scroll, and a first fixed scroll engaging the first orbiting scroll to form a first compression chamber; a second compression unit including a second orbiting scroll coupled to the second eccentric portion to enable rotation of the second orbiting scroll, and a second fixed scroll engaging the second orbiting scroll to form a second compression chamber; and a main frame disposed between the first and the second compression unit to support the first and the second compression unit, wherein a thrust plate, which supports one end of the rotating shaft to enable a thrust surface to be formed, is coupled to the inner circumference of any one of the first fixed scroll and the second fixed scroll.

Description

scroll compressor

The present invention relates to a scroll compressor, and more specifically, to a scroll compressor with a structure capable of reducing surface pressure by increasing the area supported inside a fixed scroll.

In a scroll compressor, an orbiting scroll and a non-orbiting scroll are interlocked and combined, and the orbiting scroll rotates with respect to the non-orbiting scroll to form a pair of compression chambers.

The compression chamber consists of a suction pressure chamber formed on the outside, an intermediate pressure chamber formed continuously with the volume gradually decreasing from the suction pressure chamber toward the center, and a discharge pressure chamber connected to the center of the intermediate pressure chamber. Generally, the suction pressure chamber is formed through the side surface of the non-orbiting scroll, the intermediate pressure chamber is sealed, and the discharge pressure chamber is formed through the head plate portion of the non-orbiting scroll.

Scroll compressors can be divided into low-pressure and high-pressure types depending on the path through which the refrigerant is sucked. In the low-pressure type, the refrigerant suction pipe is connected to the internal space of the casing, so that the low-temperature suction refrigerant passes through the inner space of the casing and then guided to the suction pressure chamber. In the high-pressure type, the refrigerant suction pipe is directly connected to the suction pressure chamber, so that the refrigerant flows into the internal space of the casing. This method is guided directly to the suction pressure chamber without passing through.

Patent Document 1 (KR Publication Patent No. 10-2017-0122015 (2017.11.03.)) discloses a scroll compressor of the bottom compression type, and the scroll compressor of Patent Document 1 is provided with a compression portion below the transmission unit. Additionally, an eccentric portion of the rotating shaft may be inserted into the rotating shaft coupling portion of the orbiting scroll, and the eccentric portion may be coupled to the orbiting wrap or fixed wrap so as to overlap in the radial direction of the compressor. Accordingly, an example is disclosed in which the repulsive force of the refrigerant is applied to the fixed wrap and the rotating wrap during compression, and a compressive force is applied between the rotary shaft coupling portion and the eccentric portion as a counter force.

In the case of the scroll compressor of Patent Document 1, there may be a problem that, inside the fixed scroll, when the thrust surface is damaged due to the configuration of the axial support portion including the eccentric portion, it is directly connected to damage to the compression portion and the compressor is damaged. Additionally, in the vertical direction of the Z-axis, damage may be caused to the compression section at the bottom of the shaft support portion and damage to the bearing portion at the top of the shaft support portion.

Patent Document 2 (KR Publication Patent No. 10-2016-0020190 (2016.02.23.)) discloses a scroll compressor, which includes a first scroll having a discharge port; a second scroll engaging the first scroll to form a first compression chamber and a second compression chamber; and an eccentric part eccentrically coupled to the first scroll or the second scroll, wherein the eccentric part includes a rotation axis radially overlapping with the compression chambers, and the discharge port has a discharge inlet and a discharge outlet, and the discharge inlet A scroll compressor is disclosed, which is formed in plural pieces, wherein the plurality of discharge inlets can be formed with different areas, and is capable of suppressing overcompression loss due to discharge delay by smoothly discharging refrigerant from each compression chamber.

Patent Document 3 (International Patent WO 2019-039575 A1 (2019.02.28.)) discloses a double rotation scroll type compressor. The scroll type compressor of Patent Document 3 includes a drive side scroll and a bell rotating in synchronization with the drive side scroll. It is provided with an ipsilateral scroll, and the driven shaft that supports the rotation of the driven scroll is offset by a turning radius with respect to the drive shaft that rotates the driven scroll, so that the driving shaft and the driven shaft rotate in the same direction and at the same angular speed. Additionally, Patent Document 3 discloses the feature of being restrained in the z direction through the application of a pin & ring anti-rotation structure and ball bearings.

In addition, in the case of the conventional scroll compressor, a structure was applied in which part of the supported portion (support point) inside the compression section was deleted, but the disadvantages due to support through the eccentric portion of the rotating shaft were still not improved.

More specifically, the axial support of the prior art has the following disadvantages and problems.

One problem is that the supported area is small due to the use of an eccentric part. When the local area is supported in this way, a problem occurs in which the surface pressure increases. The second problem is caused by not supporting the center of rotation. When eccentrically supported, the radius of rotation increases and the linear speed increases. The problems of the increase in surface pressure due to the above-mentioned lack of area and the increase in linear speed overlap. As a result, problems such as heat generation, seizure, and increased mechanical loss may occur.

In addition, it does not contact the entire area, but the supported area is chamfered for reasons such as bearing press-fit, so there is a possibility that the axis may get caught when moving in the z-axis direction.

Therefore, there is a need for the development of a compressor with a structure that can prevent thrust damage in the part where the shaft is supported inside the fixed scroll and damage to the compression section due to this.

The present invention was made to solve the above problems, and the purpose of the present invention is to provide a scroll compressor with a structure that can reduce surface pressure by increasing the area supported inside the fixed scroll.

In addition, another object of the present invention is to provide a scroll compressor that can solve problems of increased heat generation, seizure, and mechanical loss due to increased surface pressure and increased linear speed, which may occur due to existing eccentric support.

In addition, another object of the present invention is to provide a scroll compressor with a structure that can solve problems such as shaft jamming due to movement in the Z-axis direction.

In addition, another object of the present invention is to provide a scroll compressor with a structure that can be applied to a dual scroll compressor while complementing the shortcomings of the shaft support portion of the existing through-shaft scroll compressor.

More specifically, another object of the present invention is to provide a scroll compressor with a structure that prevents damage to the compression section by preventing the thrust surface of the rotating shaft from contacting the compression section.

In order to solve the above problems, the scroll compressor of the present invention includes a casing; A driving motor provided inside the casing; a rotation shaft rotatably coupled to the drive motor and including first and second eccentric portions spaced apart from each other; a first compression unit including a first orbiting scroll coupled to the first eccentric portion to enable rotation, and a first fixed scroll engaging the first orbital scroll to form a first compression chamber; a second compression unit including a second orbiting scroll coupled to the second eccentric portion to enable rotation, and a second fixed scroll engaging the second orbital scroll to form a second compression chamber; and a main frame disposed between the first and second compression units and supporting the first and second compression units, wherein an inner circumference of one of the first fixed scroll and the second fixed scroll has one end of the rotation shaft. A thrust plate that supports and enables the formation of a thrust surface is coupled.

With this structure, the support area becomes larger compared to a structure supported using the eccentric portion of a conventional rotation shaft. In addition, since the thrust surface is formed at the rotation center of the rotation axis, the linear speed increases as the rotation radius increases due to the existing eccentric support, thereby reducing problems of heat generation, seizure, and increased mechanical loss on the thrust surface.

The first compression unit is disposed on the opposite side of the driving motor with the second compression unit interposed therebetween, the inner circumference of the first fixed scroll accommodates one end of the rotation shaft, and the thrust plate is disposed on the first fixed scroll. It can be coupled by supporting the lower end of the rotation shaft on the inner circumference of.

Additionally, in the present invention, the thrust surface is not formed in the compressed portion, but is formed at the lower end of the rotation shaft 125, thereby preventing damage to the compressed portion.

The thrust plate may be press-fitted to the inner periphery of the first fixed scroll.

The method by which the thrust plate is press-fitted to the inner periphery of the first fixed scroll may be a muffler hot press-fitted method, and the thrust plate is more firmly coupled to the inner periphery of the first fixed scroll.

The inner circumference of the first fixed scroll may be provided with a coupling groove formed along the circumferential direction so that the outer circumference of the thrust plate can be inserted and coupled.

As a result, damage to the inner circumference of the first fixed scroll is minimized by the thrust plate, and it can be stably supported in the coupling groove.

A chamfer portion may be formed at the bottom of the inner circumference of the first fixed scroll so that the thrust plate can be retracted into the inner circumference of the first fixed scroll when the thrust plate is press-fitted.

When the thrust plate is press-fitted by the chamfer portion, interference between the inner periphery of the first fixed scroll and the thrust plate is minimized, and the thrust plate can be stably coupled.

Inside the rotating shaft, oil supply holes are formed in the axial and radial directions to supply oil to the outer periphery of the rotating shaft, and an oil pickup is communicated to enable oil to be supplied to the oil supply hole, and the oil pickup is located in the central part of the thrust plate. An oil supply communication hole may be formed to enable communication between the oil supply hole and the oil supply hole.

Due to the structure in which the oil supply communication hole is formed in the thrust plate, the oil flowing through the oil pickup can be provided to the oil supply hole of the rotating shaft, thereby smoothing the supply of oil to the sliding part.

The thrust plate may be provided with a radial oil supply groove formed in the radial direction between the oil supply communication hole and an edge of the thrust plate to communicate with the oil supply hole.

The radial oil supply grooves may be provided in plural numbers to be spaced apart from each other in the circumferential direction.

The radial oiling groove can be formed on the surface that contacts the thrust surface at the bottom of the rotating shaft, making it possible to more smoothly supply oil to the oiling hole of the rotating shaft.

The thrust plate may be provided with a circular oil supply groove formed in a circumferential direction on the outside of the oil supply hole to communicate with the oil supply hole.

As a result, oil supplied through the oil pickup can be smoothly supplied in the circumferential direction from the thrust surface of the thrust plate, and oil can be supplied more smoothly to the oil supply hole of the rotating shaft.

A coupling ring may be coupled to the inner periphery of the first fixed scroll to press and support the thrust plate on a surface opposite to the thrust surface.

As the coupling ring is installed on the thrust plate on the opposite side of the thrust surface, the coupling ring presses and supports upward from the lower surface of the thrust plate, so that the thrust plate can be more firmly coupled to the inner periphery of the first fixed scroll.

Both ends in the axial direction of the first eccentric part are disposed between the inner end of the first fixed scroll and one surface of the main frame, and both ends in the axial direction of the second eccentric part are located inside the second fixed scroll. It may be arranged to be spaced apart between the end and the other side of the main frame.

In the axial direction of the first eccentric part, the second eccentric part is spaced apart from the inner end of the second fixed scroll and the other surface of the main frame in a state in which the upward movement of the first eccentric part is restricted by the main frame. The distance may be greater than the distance in the axial direction of the second eccentric part.

In this way, even when the top of the first eccentric portion contacts the bottom of the main frame, the upper and lower ends of the second eccentric portion are spaced apart without contact between the second fixed scroll and the main frame, thereby preventing damage to the compression portion. , a clear reference point for the vertical movement of the rotation axis can be presented.

The first fixed scroll is formed to protrude from the center to the bottom, and has a first bearing protrusion on the inner circumference for receiving the rotation shaft to be inserted, and the scroll compressor of the present invention is coupled to the lower end of the first bearing protrusion. It may further include a discharge cover having an end and receiving and discharging the refrigerant discharged from the first compression chamber, wherein the coupling end may include a thrust support portion provided at an upper end of the coupling end to support the thrust plate. .

With this structure, a reference is secured for the lowest cross-section of the rotation axis 125 based on the thrust plate, and a part that accepts tolerance for the upper part is secured.

In addition, since the thrust plate is supported against the center of the rotation axis, a smaller linear speed can be secured than in previous developments.

A first bearing is installed on the outer periphery of the rotating shaft disposed on the inner periphery of the first fixed scroll, and an edge of the thrust surface of the thrust plate may be contacted by the first bearing.

By forming a structure that is contacted and supported by the first bearing at the side of the thrust plate, deformation of the portion supported at the lower end of the rotation shaft is prevented and the thrust plate can be stably supported.

In the present invention, since the thrust plate supports one end of the rotation shaft to form a thrust surface, the support area is larger than a conventional structure supported using an eccentric portion of the rotation shaft. In addition, since the thrust surface is formed at the rotation center of the rotation axis, the linear speed increases as the rotation radius increases due to the existing eccentric support, thereby reducing problems of heat generation, seizure, and increased mechanical loss on the thrust surface.

In addition, according to the present invention, as the thrust plate is provided with a radial oil supply groove, the oil supplied through the oil pickup can be smoothly supplied in the radial direction from the thrust surface of the thrust plate, and can be supplied to the oil supply hole of the rotating shaft. The supply of oil can become more smooth.

In addition, according to the present invention, as the thrust plate is provided with a circular oil supply groove, the oil supplied through the oil pickup can be smoothly supplied in the circumferential direction from the thrust surface of the thrust plate, and can be supplied to the oil supply hole of the rotating shaft. The supply of oil can become more smooth.

In addition, the present invention supports a thrust plate relative to the center of the rotation axis, so it is possible to secure a smaller linear speed than previous developments.

In addition, the present invention forms a structure in which the side of the thrust plate is contacted and supported by the first bearing, so that the thrust plate can be stably supported by preventing deformation of the portion supported at the lower end of the rotation shaft.

In addition, in the present invention, even when the upper end of the first eccentric part contacts the lower end of the main frame, the upper and lower ends of the second eccentric part are spaced apart without contact between the second fixed scroll and the main frame, preventing damage to the compression part. This can be prevented, and a clear reference point for the vertical movement of the rotation axis can be presented.

1 is a cross-sectional view showing a double scroll compressor of the present invention.

Figure 2 is an exploded perspective view showing the first and second compression units and the main frame of the present invention, viewed from the top.

Figure 3 is an exploded perspective view showing the first and second compression units and the main frame of the present invention, viewed from the bottom.

Figure 4 is an enlarged cross-sectional view showing the first and second compression units and the main frame of the present invention.

Figure 5 is an exploded perspective view showing an example in which a thrust plate is installed at the lower end of the rotation axis on the inner periphery of the first fixed scroll.

Figure 6 is a perspective view showing a thrust plate having an oil supply hole, a radial oil supply groove, and a circular oil supply groove.

Hereinafter, the scroll compressor 100 related to the present invention will be described in more detail with reference to the drawings.

In this specification, identical or similar reference numbers are assigned to identical or similar components even in different embodiments, and overlapping descriptions thereof are omitted.

In addition, even if the embodiments are different from each other, the structure applied to one embodiment may be equally applied to another embodiment as long as there is no structural or functional contradiction.

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

In describing the embodiments disclosed in this specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in this specification, the detailed descriptions will be omitted.

The attached drawings are only for easy understanding of the embodiments disclosed in this specification, and the technical idea disclosed in this specification is not limited by the attached drawings, and all changes, equivalents, and changes included in the spirit and technical scope of the present invention are not limited. It should be understood to include water or substitutes.

Figure 1 is a cross-sectional view showing the double scroll compressor 100 of the present invention, and Figure 2 is an exploded view of the first and second compression units (C1, C2) and the main frame 130 of the present invention, viewed from the upper side. This is an exploded perspective view.

In addition, Figure 3 is an exploded perspective view of the first and second compression units C1 and C2 and the main frame 130 of the present invention, and Figure 4 is an exploded perspective view of the first and second compression units C1 and C2 of the present invention. This is an enlarged cross-sectional view showing the compression units (C1, C2) and the main frame 130.

Figure 5 is an exploded perspective view showing an example in which the thrust plate 180 is installed at the lower end of the rotating shaft 125 on the inner periphery of the first fixed scroll 141, and Figure 6 shows the oil supply hole 126 and the radial oil supply groove 183. and a perspective view showing a thrust plate 180 having a circular oil supply groove 185.

Hereinafter, the scroll compressor 100 according to this embodiment will be described in detail based on an embodiment shown in the accompanying drawings.

The scroll compressor 100 of the present invention includes a casing 110, a drive motor 120, a rotating shaft 125, first and second compression units C1 and C2, and a main frame 130.

The drive motor 120 is provided inside the casing 110.

The rotation shaft 125 is rotatably coupled to the drive motor 120. The rotation shaft 125 includes first and second

eccentric portions

1255 and 1256 that are spaced apart from each other. The first and second

eccentric portions

1255 and 1256 enable the first orbiting scroll 151 and the second orbiting scroll 152, which will be described later, to pivot and rotate, respectively.

The first compression unit (C1) includes a first orbiting scroll (151) and a first fixed scroll (141).

The first orbital scroll 151 is coupled to the first eccentric portion 1255 to enable rotation. The first fixed scroll 141 engages with the first orbiting scroll 151 to form a first compression chamber V1.

The second compression unit (C2) includes a second orbiting scroll (152) and a second fixed scroll (142).

The second orbital scroll 152 is coupled to the second eccentric portion 1256 to enable rotation. The second fixed scroll 142 engages with the second orbiting scroll 152 to form a second compression chamber V2.

The main frame 130 is disposed between the first and second compression units C1 and C2 and supports the first and second compression units C1 and C2.

The first compression unit (C1) is disposed on the opposite side of the driving motor 120 with the second compression unit (C2) interposed therebetween. At this time, the inner circumference of the first fixed scroll 141 accommodates one end of the rotation shaft 125.

A thrust plate 180 is coupled to the inner circumference of the first fixed scroll 141 to support one end of the rotation shaft 125 to form a thrust surface.

The thrust surface formed by the thrust plate 180 mainly described in the present invention can be understood as a surface in contact between the lower end of the rotation axis 125 and the upper surface of the thrust plate 180 in FIGS. 1 and 4. there is.

The detailed structures of the first and second compression units C1 and C2, the main frame 130, and the rotation shaft 125 will be described later.

Meanwhile, in the present invention, the scroll compressor 100 may be a double scroll compressor 100 including first and second compression units C1 and C2.

The double scroll compressor 100 (hereinafter abbreviated as scroll compressor 100) according to this embodiment has a drive motor 120 forming a transmission unit installed in the upper half of the casing 110, and the drive motor 120 ), a first compression unit (C1), a main frame 130, and a second compression unit (C2) are provided on one side, respectively.

The drive motor 120 forming the electric transmission unit is coupled to the upper end of the rotating shaft 125, which will be described later, and the first compression unit C1 and the second compression unit C2 are sequentially coupled to the lower end of the rotating shaft 125. Accordingly, the compressor has the lower compression structure described above, and the first compression unit (C1) and the second compression unit (C2) are coupled to the drive motor 120 by one rotation shaft 125 and operate at the same speed. do.

Referring to FIG. 1, the casing 110 according to this embodiment may include a cylindrical shell 111, an upper shell 112, and a lower shell 113. The cylindrical shell 111 has a cylindrical shape with openings at both top and bottom ends, the upper shell 112 is coupled to cover the open top of the cylindrical shell 111, and the lower shell 113 is the opening of the cylindrical shell 111. It is combined to cover the bottom. Accordingly, the internal space 110a of the casing 110 is sealed, and the sealed internal space 110a of the casing 110 is divided into a lower space (S1) and an upper space (S2) based on the driving motor 120. do.

The lower space (S1) is a space formed below the driving motor 120, and the lower space (S1) is based on the compression section (C) including the first compression section (C1) and the second compression section (C2). It can be divided into storage space (S11) and discharge space (S12).

The oil storage space (S11) is a space formed on the lower side of the compression section (C), and forms a space where mixed oil containing oil or liquid refrigerant is stored. The discharge space (S12) is a space formed between the upper surface of the compression unit (C) and the lower surface of the drive motor 120, and forms a space where the refrigerant compressed in the compression unit (C) or a mixed refrigerant mixed with oil is discharged. .

The upper space (S2) is a space formed on the upper side of the drive motor 120, and forms an oil separation space where oil is separated from the refrigerant discharged from the compression unit (C). A refrigerant discharge pipe 116 communicates with the upper space S2.

The lower space (S1) and the upper space (S2) may be communicated through an internal passage passing through the internal space (110a) of the casing 110, or may be communicated through an external passage passing through the outside of the casing 110. there is.

A main frame 130 is disposed between the first compression unit (C1) and the second compression unit (C2). The main frame 130 is fixed to the inner circumference of the casing 110 and is attached to the lower and upper surfaces of the main frame 130. A structure is formed to support the first and second compression portions C1 and C2, respectively.

A refrigerant suction pipe 115 penetrates and is coupled to the side of the cylindrical shell 111. Accordingly, the refrigerant suction pipe 115 penetrates the cylindrical shell 111 forming the casing 110 in the radial direction and is coupled thereto.

The refrigerant suction pipe 115 may be formed in an F-shape with one inlet and two outlets.

For example, referring to FIGS. 1 to 4 together, the refrigerant suction pipe 115 forming the inlet is connected at one end to a refrigerant pipe (not shown) extending from the evaporator (not shown), and the refrigerant suction pipe 115 forming the outlet is connected to the refrigerant suction pipe 115 forming the outlet. The other end of 115) is separated into a first suction pipe 1151 and a second suction pipe 1152, so that the first suction pipe 1151 is connected to the first suction port 1412a, which will be described later, and the second suction pipe 1152 is connected to the second suction port, which will be described later. Each is connected to (1422a). Accordingly, the refrigerant is directly sucked into the first compression chamber (V1) and the second compression chamber (V2) through the first suction pipe 1151 and the second suction pipe 1152, respectively.

At the top of the upper shell 112, the inner end of the refrigerant discharge pipe 116 is connected to the inner space 110a of the casing 110, specifically, the upper space S2 formed on the upper side of the drive motor 120. It penetrates and joins.

One end of an oil circulation pipe (not shown) may be coupled to the lower half of the lower shell 113 in the radial direction. The oil circulation pipe is open at both ends, and the other end of the oil circulation pipe may be coupled through the refrigerant suction pipe 115. An oil circulation valve (not shown) may be installed in the middle of the oil circulation pipe.

Referring to FIG. 1, the drive motor 120 according to this embodiment includes a stator 121 and a rotor 122. The stator 121 is inserted and fixed to the inner peripheral surface of the cylindrical shell 111, and the rotor 122 is rotatably provided inside the stator 121.

The stator 121 includes a stator core 1211 and a stator coil 1212.

The stator core 1211 is formed in an annular or hollow cylindrical shape and is fixed to the inner peripheral surface of the cylindrical shell 111 by hot pressing. The outer peripheral surface of the stator core 1211 is cut or recessed in a D-cut shape along the axial direction so that the oil separated in the upper space (S2) can be recovered into the reservoir space (S11).

The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source through a power cable 1141 penetratingly coupled to the casing 110. A refrigerant passage (not indicated) is formed between the stator core 1211 and the stator coil 1212 so that the refrigerant discharged from the first compression section C1 moves to the upper space S2.

The rotor 122 includes a rotor core 1221 and a permanent magnet 1222.

The rotor core 1221 is formed in a cylindrical shape and is rotatably accommodated with a preset gap at the center of the stator core 1211. Accordingly, the gap between the stator core 1211 and the rotor core 1221 forms a refrigerant passage (not marked).

The permanent magnet 1222 is embedded along the edge of the rotor core 1221, and the upper end of the rotation shaft 125 is coupled to the center of the rotor core 1221. Accordingly, the rotation shaft 125 rotates together with the rotor 122 and transmits the rotational force of the drive motor 120 to the first orbiting scroll 151 and the second orbiting scroll 152 forming the compression portion C.

The rotation shaft 125 includes a main shaft portion 1251, a first bearing portion 1252, a second bearing portion 1253, an extension portion 1254, a first eccentric portion 1255, and a second eccentric portion 1256. do. The first bearing part 1252, the second bearing part 1253, and the shaft alignment part 1254 are formed on the same axis as the main shaft part 1251, and the first eccentric part 1255 and the second eccentric part 1256 ) is formed on an axis different from the main shaft portion 1251. Accordingly, when the rotation shaft 125 rotates, the first eccentric portion 1255 and the second eccentric portion 1256 rotate eccentrically with respect to the axial center O of the rotation shaft 125.

As shown in FIGS. 1 and 4, a first bearing 1252a is formed between the outer periphery of the first bearing part 1252 and the first bearing protrusion 1413 of the first fixed scroll 141, and the second bearing part A second bearing (1253a) is coupled between (1253) and the second bearing protrusion 1423 of the second fixed scroll 142, and is connected between the first eccentric portion 1255 and the inner circumference of the first orbiting scroll 151. An example is shown in which the third bearing (1255a) and the fourth bearing (1256a) are coupled and installed between the second eccentric portion (1256) and the inner periphery of the second orbiting scroll (152). The first to

fourth bearings

1252a, 1253a, 1255a, and 1256a may be bearing members made of journal bearings, bush bearings, or ball bearings.

The first eccentric portion 1255 is inserted into the inner periphery of the first orbiting scroll 151, and may be formed to protrude in the radial direction between the first fixed scroll 141 and the main frame 130.

For example, the first eccentric portion 1255 is the upper surface of the first head plate portion 1411 of the first fixed scroll 141 (the surface facing the first compression chamber V1) and the lower surface of the main frame 130. It may be formed to protrude in the radial direction.

The lower end of the first eccentric portion 1255 is spaced apart from the first fixed scroll 141 by a predetermined distance. In addition, the upper end of the first eccentric portion 1255 is spaced apart from the lower surface of the main frame 130 by a predetermined distance, and the upper movement is limited by the lower surface of the main frame 130.

The second eccentric portion 1256 is inserted into the inner periphery of the second orbiting scroll 152, and may be formed to protrude in the radial direction between the second fixed scroll 142 and the main frame 130.

For example, the second eccentric portion 1256 is formed on the lower surface of the second head plate 1421 of the second fixed scroll 142 (the surface facing the second compression chamber V2) and the lower surface of the main frame 130. It may be formed to protrude in the radial direction.

The upper end of the second eccentric portion 1256 is spaced apart from the second fixed scroll 142 by a predetermined distance. Additionally, the lower end of the second eccentric portion 1256 is spaced apart from the upper surface of the main frame 130 by a predetermined distance.

That is, both ends of the first eccentric portion 1255 in the axial direction are disposed between the inner end of the first fixed scroll 141 and one surface of the main frame 130, and the second eccentric portion 1256 Both ends in the axial direction are disposed between the inner end of the second fixed scroll 142 and the other surface of the main frame 130.

At this time, when the upper end of the first eccentric part 1255 in the axial direction is in contact with the lower end of the main frame 130, both ends of the second eccentric part 1256 in the axial direction are inside the second fixed scroll 142. It may be arranged to be spaced apart between the end and the other side of the main frame 130.

In this way, even when the top of the first eccentric portion 1255 contacts the bottom of the main frame 130, both upper and lower ends of the second eccentric portion 1256 are connected to the second fixed scroll 142 and the main frame 130. Since they are spaced apart without contact, damage to the compressed portion can be prevented, and a clear reference point for the vertical movement of the rotation axis 125 can be provided.

Meanwhile, referring to FIG. 4, in a state where the upward movement of the first eccentric portion 1255 is restricted by the main frame 130, the second eccentric portion 1256 moves from the second fixed scroll 142. To be spaced apart from the inner end and the other surface of the main frame 130, the axial distance d1 of the first eccentric portion 1255 is the axial distance of the second eccentric portion 1256 ( It can be larger than d2).

For this reason, even when the vertical movement of the first eccentric portion 1255 is restricted by the main frame 130, the upper and lower ends of the second eccentric portion 1256 are aligned with the second fixed scroll 142 and the main frame 130, respectively. can be spaced apart from each other, damage to the compression portion C can be prevented, and a clear reference point for the vertical movement of the rotation axis 125 can be presented.

Meanwhile, the main shaft portion 1251 forms the upper end of the rotating shaft 125 and is press-fitted and coupled to the rotor 122. The main shaft portion 1251 extends in the axial direction to be located on the same axis as the rotor 122. Accordingly, the main shaft 1251 rotates concentrically with the rotor 122.

The first bearing portion 1252 is formed between the main shaft portion 1251 and the first eccentric portion 1255, and the second bearing portion 1253 is formed between the second eccentric portion 1256 and the lower end of the rotating shaft 125. is formed Accordingly, the first bearing part 1252 is inserted into the first fixed scroll 141, which will be described later, and is supported in the radial direction, and the second bearing part 1253 is inserted into the second fixed scroll 142, which will be described later, and is supported in the radial direction. can be supported.

The first eccentric portion 1255 and the second eccentric portion 1256 extend from the main shaft portion 1251 to form the lower half of the rotating shaft 125, and are inserted into and coupled to the compression portion. For example, the first eccentric portion 1255 is coupled to a first compression portion (C1) to be described later, and the second eccentric portion 1256 is coupled to a second compression portion (C2) to be described later. Accordingly, the first eccentric portion 1255 and the second eccentric portion 1256 rotate at the same speed together with the main shaft portion 1251.

The first eccentric portion 1255 and the second eccentric portion 1256 may be formed on the same axis or may be formed on different axes. In other words, the first eccentric portion 1255 and the second eccentric portion 1256 may be formed to be eccentric by the same eccentric amount at the same rotation angle, or may be formed to be eccentric by different eccentric amounts at different rotation angles. In this embodiment, the first eccentric portion 1255 and the second eccentric portion 1256 are formed on the same axis, so that the first eccentric portion 1255 and the second eccentric portion 1256 are symmetrical in the axial direction. I'm doing it. Accordingly, based on the main frame 130, the first orbiting scroll 151 coupled to the first eccentric portion 1255 and the second orbiting scroll 152 coupled to the second eccentric portion 1256 are symmetrical. The behavior of the first orbiting scroll 151 and the second orbiting scroll 152 can be stabilized by receiving back pressure.

In addition, since the first and second

eccentric portions

1255 and 1256 are formed to be symmetrical in the axial direction with the main frame 130 interposed therebetween, the scroll compressor 100 of the present invention has a rotation axis 125, z A structure is formed to prevent jumping in the axial direction.

Additionally, an oil supply passage 126 is formed in a hollow shape inside the rotating shaft 125. The oil supply passage 126 may penetrate the inside of the rotating shaft 125 or may be formed by digging a groove to a preset height. In this embodiment, a groove may be formed from the bottom of the rotation shaft 125 to the mid-height, for example, the first bearing portion 1252. An oil pickup 127 for pumping the oil filled in the oil reservoir space S11 may be coupled to the lower end of the rotating shaft 125. Accordingly, the oil filled in the oil storage space (S11) is sucked to the upper end of the rotating shaft 125 through the oil pickup 127 and the oil supply passage 126 when the rotating shaft 125 rotates and lubricates the sliding portion.

The oil pickup 127 may include a cover member 1272 and a suction pipe 1271.

For example, as shown in FIG. 1, when the scroll compressor 100 of the present invention is a high-pressure type, a differential pressure oil supply system is applied, so even if the oil pickup is not equipped with a trochoid gear, etc., the pressure difference between the reservoir space and the compression section This makes it possible to absorb oil in the oil storage space and supply oil to the outer peripheral surface of the rotating shaft 125 or the compression section.

The oil supply passage 126 may be formed in the axial direction or may be formed inclined at a preset angle. This embodiment shows an example in which the oil supply passage 126 is formed to be inclined.

Accordingly, the oil pumped by the oil pickup 127 is absorbed due to centrifugal force in the oil supply passage 126 and can be smoothly supplied to the sliding part.

An oil supply hole 126 penetrating the outer peripheral surface of the rotating shaft 125 is formed in the oil supply passage 126. A plurality of oil supply holes 126 may be formed at predetermined intervals between the bottom and top of the oil supply passage 126. For example, the first oiling hole 126a is in the first bearing part 1252, the second oiling hole 126b is in the first eccentric part 1255, and the third oiling hole is in the second eccentric part 1256 ( 126c), a fourth oil supply hole 126d may be formed in the second bearing part 1253, respectively. Accordingly, the oil pumped through the oil supply passage 126 can be smoothly supplied to each bearing surface through each oil supply hole 126.

Referring to Figures 1 to 3, the compression unit (C) according to this embodiment includes a first compression unit (C1) and a second compression unit (C2).

In addition, a main frame 130 is disposed between the first compression unit (C1) and the second compression unit (C2). The main frame 130 is fixed to the inner circumference of the casing 110, and is separated from the lower and upper surfaces, respectively. It supports the first and second compression parts (C1, C2).

An Oldham ring 160 that prevents rotation of the first orbiting scroll 151 may be installed between the lower surface of the main frame 130 and the first compression portion C1.

Additionally, an Oldham ring 160 that prevents the rotation of the second orbiting scroll 152 may be installed between the upper surface of the main frame 130 and the second compression portion C2.

Referring to FIGS. 1 to 4, the main frame 130 forms a symmetrical structure with the same upper and lower surfaces so as to support the first and second compression units C1 and C2 on the upper and lower surfaces, respectively. can do.

That is, as will be described later, on the upper surface of the main frame 130, the second fixed scroll 142 is fixedly supported, the second orbiting scroll 152 is rotatably supported, and the second fixed scroll 142 and A structure forming a back pressure chamber is formed between the second orbiting scrolls (152).

On the lower surface of the main frame 130, as on the upper surface of the main frame, a back pressure chamber may be formed in the circumferential direction at the side between the first fixed scroll 141 and the first orbiting scroll 151.

Referring to Figures 1 and 4, the main frame 130 forms a first back pressure chamber 137a between the second orbiting scroll 152 and the second fixed scroll 142 on the side of the upper surface. The first back pressure chamber may be formed in an annular structure along the circumferential direction at the side of the main frame 130.

The main frame 130 forms a first back pressure chamber 171 between the first orbiting scroll 150 and the first fixed scroll 141 on the side of the lower surface. The first

back pressure chambers

137a and 171 may be formed in an annular structure along the circumferential direction at the side of the main frame 130.

In addition, scroll fixing parts 136 that can be fixed to support the fixed scroll 140 may be formed on both sides of the main frame 130. Additionally, the scroll fixing unit 136 may be provided with a fastening hole 136a that allows the fixed scroll 140 to be fixed.

The scroll fixing portion 136 may have a side wall structure that protrudes up and down in the circumferential direction on both sides of the main frame 130.

In addition, the main frame 130 includes a orbiting space 133, which is a space formed on the inside to accommodate the first and second orbiting scrolls 151 and 152 so that they can rotate, and a space of the orbiting space 133. A scroll support surface 132 is disposed around the main frame 130 and is formed to have a predetermined width on the upper surface of the main frame 130, and supports the first and second orbiting scrolls 151 and 152 so that they can rotate. Provided in each.

The main frame 130 is provided with a first back pressure chamber 137a, which is a space in which the gas discharged from the compression chamber V is accommodated.

For example, the first back pressure chamber 137a may be provided between the upper surface of the main frame 130, the lower side of the orbiting scroll 150, and the lower surface of the fixed scroll 140.

FIG. 2A shows an example in which a first back pressure chamber 137a is provided between the left and right upper surfaces of the main frame 130, both left and right sides of the orbiting scroll 150, and both bottom surfaces of the fixed scroll 140.

The first back pressure chamber 137a is shown to be provided on both left and right sides in FIG. 1, but is a space formed along the circumferential direction between the main frame 130, the orbiting scroll 150, and the fixed scroll 140. It can be understood.

In addition, Oldham rings 160 may be installed on the lower and upper surfaces of the main frame 130, respectively. The Oldham rings 160 prevent the rotation of the first orbiting scroll 151 and the second orbiting scroll 152. Let's do it.

The first compression unit (C1) and the second compression unit (C2) are provided on both sides of the main frame 130 in the axial direction. Hereinafter, the compression section (C) located on the lower side of the main frame 130 is defined as the first compression section (C1), and the compression section located on the upper side of the main frame 130 is defined as the second compression section (C2). Explain.

The first compression unit (C1) according to this embodiment includes a first fixed scroll (141) and a first orbiting scroll (151).

The first fixed scroll 141 is fixed to the inner peripheral surface of the cylindrical shell 111, and the first orbiting scroll 151 can be rotatably supported in the axial direction on the upper surface of the first fixed scroll 141. Accordingly, a pair of first compression chambers (V1) are formed between the first fixed scroll (141) and the first orbiting scroll (151) forming the first compression section (C1).

The first fixed scroll 141 may include a first bearing protrusion 1413. Referring to FIG. 3, the first bearing protrusion 1413 protrudes from the center of the first fixed scroll 141 to the bottom, and can accommodate the rotation shaft 125 to be inserted into the inner circumference.

The first bearing protrusion 1413 may be formed to extend axially from the center of the first fixed scroll 141 toward the lower shell 113. At the center of the first bearing protrusion 1413, a cylindrical first bearing hole 1413a is formed by penetrating in the axial direction, and the first bearing portion 1252 of the rotating shaft 125 is formed in the first bearing hole 1413a. It can be inserted and supported in the radial direction.

Meanwhile, the scroll compressor 100 of the present invention may further include a discharge cover 145.

The discharge cover 145 may have a coupling end 145a coupled to the lower end of the first bearing protrusion 1413. Additionally, the discharge cover 145 is coupled to the lower end of the first fixed scroll 141 and accommodates the refrigerant compressed and discharged from the first compression chamber V1.

Afterwards, the refrigerant discharged from the first compression chamber (V1) to the discharge space 1451 of the discharge cover 145 is combined with the refrigerant discharged from the second compression chamber (V2) to the internal space 110a of the casing 110. After being mixed and passing through the drive motor 120, the oil is separated in the upper space (S2).

For example, the discharge cover 145 may include a coupling end 145a and a thrust support portion 145b.

The inner side of the coupling end 145a may be coupled to the lower end of the first bearing protrusion 1413.

The coupling end 145a may be provided at the center of the discharge cover 145. In addition, the coupling end 145a may extend in the circumferential direction, and a receiving groove 145e may be formed therein to accommodate the lower end of the first bearing protrusion 1413.

The coupling end portion 145a may further be formed with a sealing groove portion 145c in which a sealing member is installed to enable sealing with the first bearing protrusion 1413.

The thrust support portion 145b may be provided on the upper portion of the coupling end portion 145a to support the thrust plate 180.

A through hole 145d to which the upper part of the oil pickup 127 is coupled may be formed on the inner periphery of the coupling end 145a.

A coupling ring 187, which will be described later, may be coupled between the thrust support portion 145b and the thrust plate 180. For example, the coupling ring 187 is coupled to the inside of the first bearing protrusion 1413 of the first fixed scroll 141 on the surface opposite to the thrust surface of the thrust plate 180 to press and support the thrust plate 180. can do.

As the coupling ring 187 is installed on the thrust plate 180 on the opposite side of the thrust surface, the thrust plate 180 can be more firmly coupled to the inner periphery of the first fixed scroll 141.

The coupling ring 187 may be a C ring, for example. Figure 5 shows an example of a C-ring coupling ring 187. The coupling ring 187 has an elastic opening 187c and can be elastically deformed, so that it is attached to the inner circumference of the first fixed scroll 141. Can be elastically combined.

With this structure, a reference is secured for the lowest cross-section of the rotation axis 125 based on the thrust plate 180, and a part that accepts tolerance for the upper part is secured.

In addition, since the thrust plate 180 is supported with respect to the center of the rotation axis 125, a smaller linear speed can be secured than in previous developments.

The first fixed scroll 141 according to this embodiment may include a first fixed head plate 1411, a first fixed side wall 1412, a first bearing protrusion 1413, and a first fixed wrap 1414. there is.

The first fixing plate portion 1411 is formed in a disk shape, and a first bearing hole 1413a forming a first bearing protrusion 1413, which will be described later, is formed through the center in the axial direction.

A first discharge port 1411a is formed around the first bearing hole 1413a, which will be described later, and the first discharge port 1411a is a discharge cover fixed to the second side (lower surface) of the first fixed end plate portion 1411. It is formed to open toward the discharge space 1451 of 145). Accordingly, the refrigerant compressed in the first compression chamber (V1) is discharged into the discharge space (1451) of the discharge cover (145) through the first discharge port (1411a).

The first fixed side wall portion 1412 extends axially from the first side (top surface) edge of the first fixed head plate portion 1411 toward the first orbital plate portion 1511 of the first orbital scroll 151 and has an annular shape. can be formed. Accordingly, the first pivoting plate portion 1511 can be supported in the axial direction on the first fixed side wall portion 1412 so that it can pivot.

A first suction port 1412a is formed in the first fixed side wall portion 1412 in the radial direction. The end of the first suction pipe 1151 penetrating the cylindrical shell 111 is inserted and coupled to the first suction port 1412a as described above. Accordingly, a portion of the refrigerant discharged from the evaporator is sucked into the first compression chamber (V1) through the first suction pipe 1151 and the first suction port 1421a of the refrigerant suction pipe 115.

The first bearing protrusion 1413 extends axially from the center of the first fixed head plate 1411 toward the lower shell 113. At the center of the first bearing protrusion 1413, a cylindrical first bearing hole 1413a is formed by penetrating in the axial direction, and the first bearing portion 1252 of the rotating shaft 125 is formed in the first bearing hole 1413a. It can be inserted and supported in the radial direction.

As described above, the inner circumference of the first fixed scroll 141 accommodates one end of the rotation shaft 125. In addition, a thrust plate 180 is coupled to the inner periphery of the first fixed scroll 141 to support one end of the rotation shaft 125 to form a thrust surface.

In the present invention, since the thrust plate 180 supports one end of the rotation shaft 125 to form a thrust surface, the support area is increased compared to a conventional structure supported using an eccentric portion of the rotation shaft 125. In addition, since the thrust surface is formed at the rotation center of the rotation axis 125, the linear speed increases as the rotation radius increases due to the existing eccentric support, thereby reducing the problems of heat generation, seizure, and increased mechanical loss on the thrust surface. .

As shown in FIG. 4, an example is of accommodating the lower end of the first bearing portion of the rotating shaft 125 on the inner periphery of the first bearing hole 1413a at the center of the first bearing protrusion 1413 of the first fixed scroll 141. It is shown.

In addition, an example is shown in which the thrust plate 180 is coupled to the inner circumference of the first bearing hole 1413a to support the lower end of the first bearing part of the rotating shaft 125, and the lower end of the first bearing part of the rotating shaft 125 and the thrust A thrust surface is formed between the upper surfaces of the plates 180.

The thrust plate 180 may be press-fitted to the inner periphery of the first fixed scroll 141. For example, as shown in FIGS. 4 and 5, the thrust plate 180 may be press-fitted to the inner periphery of the first bearing hole 1413a of the first bearing protrusion 1413.

Additionally, a coupling groove 1413b may be provided on the inner circumference of the first fixed scroll 141 so that the outer circumference of the thrust plate 180 can be inserted and coupled.

A chamfer portion 1413b may be formed at the bottom of the inner circumference of the first fixed scroll 141 so that the thrust plate 180 can be inserted into the inner circumference of the first fixed scroll 141 when the thrust plate 180 is press-fitted.

Additionally, an oil supply communication hole 181 is formed in the thrust plate 180. The oil supply communication hole 181 allows communication between the oil pickup and the oil supply hole 126 inside the rotating shaft 125, so that the oil in the reservoir space is discharged through the oil pickup 127 through the oil supply communication hole 181. 126).

The oil supply communication hole 181 may be formed at the center of the thrust plate 180. Additionally, the oil supply communication hole 181 may be formed penetrating the thrust plate 180.

The thrust plate 180 may also be provided with a radial oiling groove 183. The radial oil supply groove 183 may be formed in the radial direction between the oil supply communication hole 181 and the edge of the thrust plate 180 to communicate with the oil supply hole 126.

The radius oil supply groove 183 can be formed on the surface contacting the bottom of the rotary shaft 125, so that oil can be supplied more smoothly to the oil supply hole 126 of the rotary shaft 125.

A plurality of radial oiling grooves 183 may be provided to be spaced apart from each other in the circumferential direction.

Figure 6 shows an example in which three radial oil supply grooves 183 are arranged to be spaced apart from each other at equal intervals in the circumferential direction.

The thrust plate 180 may be provided with a circular oil supply groove 185.

The circular oil supply groove 185 may be formed in the circumferential direction on the outside of the oil supply hole 126 to communicate with the oil supply hole 126.

As the thrust plate 180 is provided with a radial oil supply groove 183, the oil supplied through the oil pickup can be smoothly supplied in the radial direction from the thrust surface of the thrust plate 180, and the rotating shaft ( The supply of oil to the oil supply hole 126 of 125) can be made more smooth.

In addition, as the thrust plate 180 is provided with a circular oil supply groove 185, the oil supplied through the oil pickup can be smoothly supplied in the circumferential direction from the thrust surface of the thrust plate 180, The supply of oil to the oil supply hole 126 of the rotating shaft 125 can be made more smooth.

Additionally, referring to FIG. 4, the first bearing 1252a may be in contact with the edge of the thrust surface of the thrust plate 180.

By forming a structure in which the first bearing 1252a contacts and supports the side of the thrust plate 180, the thrust plate 180 is prevented from deforming the portion supported at the lower end of the rotation shaft 125 and is stably maintained. It can be supported.

Meanwhile, a coupling ring 187 may be coupled to the inner periphery of the first fixed scroll 141 to press and support the thrust plate 180 on the opposite side of the thrust surface. For example, the coupling ring 187 is coupled to the inside of the first bearing protrusion 1413 of the first fixed scroll 141 on the surface opposite to the thrust surface of the thrust plate 180 to press and support the thrust plate 180. can do.

As the coupling ring 187 is installed on the thrust plate 180 on the opposite side of the thrust surface, the thrust plate 180 can be more firmly coupled to the inner circumference of the first fixed scroll 141.

The coupling ring 187 may be, for example, a C ring.

The first bearing hole 1413a is formed on the same axis as the second bearing hole 1423a, which will be described later. The above-described first bearing is provided on the inner peripheral surface of the first bearing hole 1413a to support the first bearing portion 1252 of the rotating shaft 125.

The first fixing wrap 1414 may be formed to extend axially from the upper surface of the first fixing head plate portion 1411 toward the first orbiting scroll 151. The first fixed wrap 1414 engages with the first pivoting wrap 1512, which will be described later, to form a pair of first compression chambers V1.

The first fixing wrap 1414 may be formed in an involute shape. However, the first fixed wrap 1414, together with the first swing wrap 1512, may be formed in various shapes other than an involute.

For example, the first fixed wrap 1414 has a shape of connecting a plurality of circular arcs with different diameters and origins, and the outermost curve may be formed in an approximately elliptical shape with a major axis and a minor axis. The first orbital wrap 1512 may also be formed in an involute shape, and may be formed in an arc connection shape in addition to the involute shape.

Referring to Figures 1 to 3, the first turning scroll 151 according to the present embodiment may include a first turning mirror plate part 1511, a first turning wrap 1512, and a first rotating shaft engaging part 1513. You can.

The first pivot plate portion 1511 is formed in a disk shape, and a first pivot wrap 1512 is formed in the center of the lower surface, and the bottom edge of the first pivot disk portion 1511 is on the upper surface of the first fixed scroll 141. It is supported axially. Accordingly, while the first swing wrap 1512 is engaged with the first fixed wrap 1414, the first pivot plate portion 1511 is supported by the first fixed scroll 141 and makes a pivot movement.

Additionally, an annular back pressure chamber 171 may be formed between the first pivot plate portion 1511 and the main frame 130 facing it. Accordingly, the first pivot plate portion 1511 is axially supported in the direction toward the first fixed scroll 141 with respect to the main frame 130, effectively suppressing leakage between compression chambers in the first compression chamber (V1). You can.

A back pressure chamber (137a) may also be formed between the second pivot plate portion and the main frame 130 facing it, and a back pressure chamber (137a) between the first pivot disk portion 1511 and the main frame 130 facing it ( 170) will be replaced with an explanation.

Specifically, a first sealing groove 1511e is formed on the back of the first pivot plate portion 1511 at a preset distance in the radial direction, and a sealing member is inserted into the first sealing groove 1511e.

Accordingly, a back pressure chamber is formed outside the sealing member inserted into the first sealing groove 1511e, between the main frame 130, and on the side and top of the first orbiting scroll 151.

The first swing wrap 1512 may be formed to extend from the second side (lower surface) of the first pivot plate portion 1511 toward the first fixed scroll 141. The first orbital wrap 1512 engages with the first fixed wrap 1414 to form the first compression chamber V1.

The first orbital wrap 1512 is formed to correspond to the shape of the first fixed wrap 1414 described above. Like the first fixed wrap 1414, it may be formed in an involute shape, or in the shape of an arc. can also be formed.

However, the inner end of the first pivot wrap 1512 is formed at the center of the first pivot plate 1511, and the first rotation shaft engaging portion 1513 is formed at the center of the first pivot plate 1511 in the axial direction. It can be formed through.

The first eccentric portion 1255 of the rotation shaft 125 is rotatably inserted and coupled to the first rotation shaft coupling portion 1513. The outer periphery of the first rotation shaft coupling portion 1513 is connected to the first turning wrap 1512 and serves to form the first compression chamber V1 together with the first fixed wrap 1414 during the compression process.

The first rotation shaft coupling portion 1513 may be formed at a height that overlaps the first pivot wrap 1512 on the same plane. That is, the first rotation shaft coupling portion 1513 may be disposed at a height where the first eccentric portion 1255 of the rotation shaft 125 overlaps the first pivot wrap 1512 on the same plane. Accordingly, the repulsion force and compression force of the refrigerant are applied to the same plane based on the first orbital plate portion 1511 and cancel each other out, thereby suppressing the tilt of the first orbital scroll 151 due to the action of the compression force and repulsion force. It can be.

Referring again to FIGS. 1 to 3, the second compression unit (C2) according to this embodiment is provided on the upper side of the main frame 130, and the second compression unit (C2) is the first compression unit (C1). is formed symmetrically. For example, the second compression unit C2 includes a second fixed scroll 142 and a second orbiting scroll 152.

Meanwhile, as described above, the first compression unit C1 is provided on the lower side of the main frame 130.

The second fixed scroll 142 is fixed to the inner peripheral surface of the cylindrical shell 111 from the upper side of the main frame 130, and the second orbiting scroll 152 is rotatable on the back of the second fixed scroll 142 in the axial direction. can be supported. Accordingly, a pair of second compression chambers (V2) are formed between the second fixed scroll (142) and the second orbiting scroll (152) forming the second compression portion (C2).

The second fixed scroll 142 according to this embodiment may include a second fixed head plate 1421, a second fixed side wall 1422, a second bearing protrusion 1423, and a second fixed wrap 1424. there is.

The second fixing plate portion 1421 is formed in a disk shape, and in the center, a second bearing hole 1423a forming a second bearing protrusion 1423, which will be described later, is formed through penetrating in the axial direction. A second discharge port 1421a is formed around the second bearing hole 1423a. The second discharge port 1421a is formed to be located on the same axis as the first discharge port 1411a, that is, at the same rotation angle.

The second discharge port 1421a is formed to communicate between the second compression chamber V2 and the internal space 110a of the casing 110. Accordingly, the refrigerant compressed in the second compression chamber (V2) is discharged into the internal space (110a) of the casing (110) through the second discharge port (1421a).

The second fixed side wall portion 1422 extends axially from the edge of the first side (lower surface) of the second fixed head plate portion 1421 toward the second orbital plate portion 1521 of the second orbital scroll 152, which will be described later. It can be formed into a ring shape. Accordingly, the second pivoting plate portion 1521 can be supported in the axial direction on the second fixed side wall portion 1422 so that it can pivot.

A second suction port 1422a is formed in the second fixed side wall portion 1422 in the radial direction. The second suction port 1422a is formed to be located on the same axis as the first suction port 1412a, that is, at the same rotation angle.

The end of the second suction pipe 1152 penetrating the cylindrical shell 111 is inserted and coupled to the second suction port 1422a as described above. Accordingly, part of the refrigerant discharged from the evaporator is sucked into the second compression chamber (V2) through the second suction pipe 1152 and the second suction port 1422a of the refrigerant suction pipe 115.

The second bearing protrusion 1423 extends axially from the center of the second fixed head plate 1421 toward the drive motor 120. At the center of the second bearing protrusion 1423, a cylindrical second bearing hole 1423a is formed by penetrating in the axial direction, and the second bearing portion 1253 of the rotating shaft 125 is formed in the second bearing hole 1423a. It can be inserted and supported in the radial direction.

The second bearing hole 1423a is formed on the same axis as the bearing receiving portion 133 of the main frame 130 and the first bearing hole 1413a. A bearing member made of a bush bearing or ball bearing, etc. is provided on the inner peripheral surface of the second bearing hole 1423a to support the second bearing portion 1253 of the rotating shaft 125.

The second fixing wrap 1424 may be formed to extend axially from the lower surface of the second fixing head plate portion 1421 toward the second orbiting scroll 152. The second fixed wrap 1424 engages with the second pivoting wrap 1522, which will be described later, to form a pair of second compression chambers V2.

The second fixing wrap 1424 may be formed in an involute shape. However, the second fixed wrap 1424, together with the second swing wrap 1522, may be formed in various shapes other than the involute. For example, the second fixed wrap 1424 has a shape of connecting a plurality of circular arcs with different diameters and origins, and the outermost curve may be formed in an approximately elliptical shape with a major axis and a minor axis. The second orbital wrap 1522 may also be formed in the same way.

Additionally, the second fixed wrap 1424 is formed to be symmetrical to the first fixed wrap 1414 described above. In other words, the second fixed wrap 1424 is formed identically to the first fixed wrap 1414 when projected in the axial direction (or along the axial direction). Accordingly, the second suction port 1422a may be formed on the same axis as the first suction port 1412a, and the second discharge port 1421a may be formed at the same rotation angle as the first discharge port 1411a.

Referring again to Figures 1 to 4, the second turning scroll 152 according to this embodiment includes a second turning plate part 1521, a second turning wrap 1522, and a second rotating shaft engaging part 1523. do.

The second swing wrap 1522 is formed extending from the second side (top surface) of the second pivot plate portion 1521 toward the second fixed scroll 142. The second orbital wrap 1522 engages with the second fixed wrap 1424 to form a second compression chamber V2.

Since the second orbital wrap 1522 is formed to correspond to the shape of the second fixed wrap 1424 described above, the description of the second orbital wrap 1522 will be replaced with the second fixed wrap 1424. However, the inner end of the second pivot wrap 1522 is formed in the central portion of the second pivot plate portion 1521, and the second rotation shaft engaging portion 1523 is formed in the central portion of the second pivot plate portion 1521 in the axial direction. It can be formed through.

Additionally, the second orbital wrap 1522 is formed to be symmetrical to the first orbital wrap 1512 described above. In other words, as the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 are formed on the same axis, the second pivoting wrap 1522 is formed along the axial direction with the first pivoting wrap 1512. are formed identically. Accordingly, the second suction port 1422a may be formed on the same axis as the first suction port 1412a, and the second discharge port 1421a may be formed at the same rotation angle as the first discharge port 1411a.

The second eccentric portion 1256 of the rotation shaft 125 is rotatably inserted and coupled to the second rotation shaft coupling portion 1523. The outer periphery of the second rotation shaft coupling portion 1523 is connected to the second turning wrap 1522 and serves to form the second compression chamber V2 together with the second fixed wrap 1424 during the compression process.

The second rotation shaft coupling portion 1523 may be formed at a height that overlaps the second pivot wrap 1522 on the same plane. That is, the second rotation shaft coupling portion 1523 may be disposed at a height where the second eccentric portion 1256 of the rotation shaft 125 overlaps the second pivot wrap 1522 on the same plane. Accordingly, the repulsion force and compression force of the refrigerant are applied to the same plane based on the second orbital plate portion 1521 and cancel each other out, thereby suppressing the tilt of the second orbital scroll 152 due to the action of the compression force and repulsion force. It can be.

The scroll compressor 100 according to this embodiment as described above operates as follows.

That is, when power is applied to the drive motor 120, a rotational force is generated in the drive motor 120, causing the rotor 122 to rotate. Then, the rotation shaft 125 coupled to the rotor 122 rotates, and the first orbiting scroll 151 coupled to the first eccentric portion 1255 of the rotation shaft 125 is supported by the main frame 130, A turning movement is performed with respect to the first fixed scroll (141). At the same time, the second orbital scroll 152 coupled to the second eccentric portion 1256 of the rotation shaft 125 is supported by the main frame 130 and makes a orbital movement with respect to the second fixed scroll 142.

Then, the volumes of the first compression chamber (V1) and the second compression chamber (V2) are increased in each suction pressure chamber (not marked) formed outside the first and second compression chambers (V2) (V1, V2). It gradually decreases toward each intermediate pressure chamber (not marked) formed continuously toward the center, and the discharge pressure chamber (not marked) formed at the center.

Then, the refrigerant that has passed through the refrigeration cycle device passes through the first suction pipe 1151 of the refrigerant suction pipe 115 toward the first suction pressure chamber forming the first compression chamber V1, and passes through the second suction pipe 1152 toward the first suction pressure chamber forming the first compression chamber V1. Each is sucked toward the second suction pressure chamber forming the second compression chamber (V2).

Then, the refrigerant sucked into each suction pressure chamber is compressed while moving to each discharge pressure chamber through each intermediate pressure chamber along the movement trajectory of the first compression chamber (V1) and the second compression chamber (V2), and the first compression chamber The refrigerant compressed in the chamber (V1) passes through the first discharge port (1411a) into the discharge space (1451) of the discharge cover (145), and the refrigerant compressed in the second compression chamber (V2) passes through the second discharge port (1421a). Each is discharged into the internal space 110a of the casing 110.

Then, the refrigerant discharged from the first compression chamber (V1) to the discharge space 1451 of the discharge cover 145 is mixed with the refrigerant discharged from the second compression chamber (V2) to the internal space 110a of the casing 110. After passing through the drive motor 120, oil is separated in the upper space (S2).

Then, the refrigerant from which the oil is separated in the upper space (S2) moves toward the condenser of the refrigeration cycle through the refrigerant discharge pipe 116, and the oil separated from the refrigerant in the upper space (S2) moves to the lower space of the casing (110). It is recovered into the storage space (S11), which is (S1). This oil is supplied to each bearing surface (not marked) through the oil supply passage 126, and a series of processes in which some of it is supplied to the compression chamber (V) are repeated.

At this time, a portion of the oil pumped through the oil supply passage 126 flows through each oil supply hole 126a to 126d to the outer circumference of the rotating shaft 125 (the first bearing part 1252, the second bearing part 1253, It is supplied between the first eccentric portion 1255 and the second eccentric portion 1256) and the first to

fourth bearings

1252a, 1253a, 1255a, and 1256a.

Additionally, the pumped oil may pass through the oil supply communication hole 181 and be supplied to the oil supply hole 126 of the rotating shaft 125. At this time, on the thrust surface between the rotation shaft 125 and the thrust plate 180, the flow of oil is further promoted by the circular oil supply groove 185 and the radial oil supply groove 183.

Meanwhile, when the first and second orbiting scrolls 151 and 152 rotate by rotation of the rotation shaft 125, the conventional rotation shaft 125 is inside the first and second

fixed scrolls

141 and 142. Since the thrust plate 180 is installed at the bottom of the rotating shaft 125 without having a thrust surface like the shaft support, the area supported by the thrust surface becomes larger, reducing the increase in surface pressure and linear speed. You can.

Additionally, since the thrust surface is located at the bottom of the rotating shaft 125, damage to the compressed part can be prevented by preventing the thrust surface of the shaft from contacting the compressed part.

The scroll compressor 100 described above is not limited to the configuration and method of the embodiments described above, and the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

It is obvious to those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit and essential features of the present invention. Accordingly, the above detailed description should not be construed as restrictive in all respects and should be considered illustrative. The scope of the present invention should be determined by reasonable interpretation of the appended claims, and all changes within the equivalent scope of the present invention are included in the scope of the present invention.

The present invention can be used in a scroll compressor with a structure that can reduce surface pressure by increasing the area supported inside the fixed scroll.

Claims

casing;

A driving motor provided inside the casing;

a rotation shaft rotatably coupled to the drive motor and including first and second eccentric portions spaced apart from each other;

a first compression unit including a first orbiting scroll coupled to the first eccentric portion to enable rotation, and a first fixed scroll engaging the first orbital scroll to form a first compression chamber;

a second compression unit including a second orbiting scroll coupled to the second eccentric portion to enable rotation, and a second fixed scroll engaging the second orbital scroll to form a second compression chamber; and

A main frame disposed between the first and second compression units and supporting the first and second compression units,

A scroll compressor in which a thrust plate capable of forming a thrust surface by supporting one end of a rotating shaft is coupled to the inner circumference of one of the first fixed scroll and the second fixed scroll.
According to paragraph 1,

The first compression unit is disposed on the opposite side of the drive motor with the second compression unit interposed therebetween, and the inner circumference of the first fixed scroll accommodates one end of the rotation shaft,

The thrust plate is a scroll compressor coupled to the inner circumference of the first fixed scroll by supporting the lower end of the rotation shaft.
According to paragraph 2,

A scroll compressor wherein the thrust plate is press-fitted to the inner circumference of the first fixed scroll.
According to paragraph 3,

A scroll compressor wherein an inner circumference of the first fixed scroll is provided with a coupling groove formed along the circumferential direction so that the outer circumference of the thrust plate can be inserted and coupled.
According to paragraph 3,

A scroll compressor in which a chamfer portion is formed at the bottom of the inner circumference of the first fixed scroll so that the thrust plate can be retracted into the inner circumference of the first fixed scroll when the thrust plate is press-fitted.
According to paragraph 1,

Inside the rotating shaft, oil supply holes are formed in the axial and radial directions to supply oil to the outer periphery of the rotating shaft, and an oil pickup is communicated to enable oil to be supplied to the oil supply holes,

A scroll compressor in which an oil supply communication hole is formed in the central portion of the thrust plate to enable communication between the oil pickup and the oil supply hole.
According to clause 6,

The thrust plate is a scroll compressor having a radial oil supply groove formed in the radial direction between the oil supply communication hole and an edge of the thrust plate to communicate with the oil supply hole.
In clause 7,

A scroll compressor in which a plurality of radial oil supply grooves are provided to be spaced apart from each other in the circumferential direction.
According to clause 6,

The thrust plate is a scroll compressor having a circular oil supply groove formed in a circumferential direction on the outside of the oil supply hole to communicate with the oil supply hole.
According to paragraph 1,

A scroll compressor in which a coupling ring is coupled to the inner periphery of the first fixed scroll to press and support the thrust plate on a surface opposite to the thrust surface.
According to paragraph 2,

Both ends of the first eccentric portion in the axial direction are disposed between the inner end of the first fixed scroll and one surface of the main frame,

A scroll compressor in which both ends of the second eccentric portion in the axial direction are arranged to be spaced apart between the inner end of the second fixed scroll and the other surface of the main frame.
According to clause 11,

In the axial direction of the first eccentric part, the second eccentric part is spaced apart from the inner end of the second fixed scroll and the other surface of the main frame in a state in which the upward movement of the first eccentric part is restricted by the main frame. The distance of the scroll compressor is greater than the distance in the axial direction of the second eccentric part.
According to paragraph 2,

The first fixed scroll is formed to protrude from the center to the bottom and has a first bearing protrusion on the inner circumference for receiving the rotation shaft to be inserted,

It further includes a discharge cover having a coupling end coupled to the lower end of the first bearing protrusion and receiving and discharging the refrigerant discharged from the first compression chamber,

The coupling end is a scroll compressor including a thrust support portion provided at an upper end of the coupling end to support the thrust plate.
According to claim 2 or 13,

A first bearing is installed on the outer circumference of the rotating shaft disposed on the inner circumference of the first fixed scroll,

A scroll compressor in which an edge of the thrust surface of the thrust plate is contacted by the first bearing.