KR102541912B1 - Scroll Compressor - Google Patents

Abstract

casing; a fixed scroll installed inside the casing and equipped with a fixed wrap; an orbiting scroll having an orbiting wrap that rotates with respect to the fixed scroll and engages with the stationary wrap to form a compression chamber; a rotating shaft disposed in one direction inside the casing and installed on inner circumferences of the fixed scroll and the orbiting scroll to transmit rotational force to enable rotation of the orbiting scroll; and a swing bearing inserted between an inner circumference of the orbiting scroll and an outer circumference of the rotating shaft, wherein the orbiting scroll axially passes through an inner end of the orbiting wrap at one side of the orbiting mirror plate part and has the orbiting bearing on the inner circumference. A rotary shaft coupling portion inserted and accommodated is provided, and at least a portion of one end of the swing bearing overlaps the swing mirror plate portion in an axial direction.

Description

Scroll Compressor

The present invention relates to a scroll compressor having a structure capable of alleviating deformation and tilting of an orbiting scroll.

In the scroll compressor, an orbiting scroll and a non-orbiting scroll are interdigitated and coupled, and the orbiting scroll performs a orbital motion 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 continuously formed as the volume of the suction pressure chamber gradually decreases 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 of the non-orbiting scroll.

The scroll compressor may be classified into a low pressure type and a high pressure type according to the path through which the refrigerant is sucked. In the low-pressure type, the refrigerant suction pipe communicates with the inner space of the casing, and the low-temperature suction refrigerant passes through the inner space of the casing and is guided to the suction pressure chamber. It is a method that is directly guided to the suction pressure chamber without passing through.

The scroll compressor of the lower compression type is located on the lower side of the transmission part that transmits power so that the orbiting scroll is rotated by the compression unit composed of the fixed scroll and the orbiting scroll. A bottom compression type high-pressure compressor that discharges is often used. In this regard, it is as provided in Republic of Korea Patent Publication No. 10-2016-0020191 (Patent Document 1).

The material of the orbiting scroll, which is one component of the scroll compressor, is GC250, a type of gray cast iron. In particular, when used in an air conditioning compressor, the scroll compressor operates at 2.0 horsepower (HP) to 3.5 horsepower.

As for the position of the bearing of the scroll compressor, in the case of a model currently being mass-produced (R1 20Fr., 3.5 horsepower), the height (H) of the bearing installed inside the orbiting scroll is 20, and the height (h) of the head press-fitting part where the bearing is press-fitted is 3 and is being mass-produced at the level of H/h = 0.15.

In addition, as the material of the orbiting scroll was changed to aluminum and the horsepower increased, the height (H) of the bearing increased to 25, and the height (h) of the head press-fitting part into which the bearing was press-fitted increased to 5.8, increasing to H/h = 0.23. As the material of the orbiting scroll is changed, the strength of the orbiting scroll is weakened, and there is a problem that deformation occurs at the minimum thickness position of the boss portion where the bearing is installed in the orbiting scroll.

The change from the cast iron material of the orbiting scroll of the conventional lower compression scroll to the Al material increases the efficiency and reduces the centrifugal force of the orbiting scroll to improve high-speed efficiency. However, as the material is changed, there is a problem in that reliability and efficiency decrease in the orbiting scroll and orbiting bearing.

In particular, as the material of the orbiting scroll is changed to aluminum and the horsepower increases, there is a problem that deformation occurs at the position of the minimum thickness of the boss portion where the bearing of the orbiting scroll is installed, and the bearing deformation at this position after the scroll compressor is operated During over-operation, the center of gravity of the bearing installed on the inner circumference of the orbiting scroll is located far from the compression chamber, resulting in a tilting phenomenon of the orbiting scroll.

In addition, it is preferable that the length of the bearing installed in the orbiting scroll is the same as that of the orbiting wrap so that both ends of the bearing coincide with both ends of the orbiting wrap. In this case, the root of the orbiting wrap (near the orbiting mirror plate) Deformation or damage may occur.

It is required to develop a structure capable of alleviating the deformation and tilting of the orbiting scroll generated during the refrigerant compression operation in the compression unit by selecting the optimal position of the bearing.

Republic of Korea Patent Publication No. 10-2016-0020191

The present invention has been made to solve the above problems, and one object of the present invention is to provide a scroll compressor capable of mitigating a tilting phenomenon of an orbiting scroll in a compression unit that may occur during operation of the scroll compressor.

Another object of the present invention is to provide a scroll compressor having a structure capable of reducing deformation in an orbiting mirror plate portion of an orbiting scroll.

Another object of the present invention is to provide a scroll compressor that alleviates a tilting phenomenon of an orbiting scroll by minimizing a height difference between a center where pressure acts in a compression chamber and a support point of a swing bearing supporting the center.

Another object of the present invention is to provide a scroll compressor in which one end of the orbiting bearing is disposed to overlap the orbiting head plate to suppress deformation or damage in an orbiting wrap portion of the orbiting scroll.

In order to solve the above problems, the scroll compressor of the present invention, the casing; a fixed scroll installed inside the casing and equipped with a fixed wrap; an orbiting scroll having an orbiting wrap that rotates with respect to the fixed scroll and engages with the stationary wrap to form a compression chamber; a rotating shaft disposed in one direction inside the casing and installed on inner circumferences of the fixed scroll and the orbiting scroll to transmit rotational force to enable rotation of the orbiting scroll; and a swing bearing inserted between an inner circumference of the orbiting scroll and an outer circumference of the rotating shaft, wherein the orbiting scroll axially passes through an inner end of the orbiting wrap at one side of the orbiting mirror plate part and has the orbiting bearing on the inner circumference. A rotary shaft coupling portion inserted and accommodated is provided, and at least a portion of one end of the swing bearing overlaps the swing mirror plate portion in the axial direction.

In the scroll compressor of the present invention, one end of the swing bearing is inserted into the inner circumference of the orbiting scroll so that it is disposed at a portion of the predetermined width of the orbiting head plate portion, so that the center of gravity of the orbiting bearing is lower than the compression chamber. Tilting occurrence can be reduced.

An overlapping length (h) between the swing bearing and the swing mirror plate is 0.1 to 0.3 relative to the height (H) of the swing bearing.

An overlapping length (h) between the swing bearing and the swing mirror plate part is 0.2 to 0.4 relative to the thickness (W) of the swing mirror plate part.

In addition, in the scroll compressor of the present invention, one end of the orbiting bearing is inserted into the inner circumference of the orbiting scroll so as to be disposed at a portion of the predetermined width of the orbiting head plate, so that the occurrence of deformation on the inner circumference of the orbiting head plate is also reduced.

An overlap length (h) between the swing bearing and the swing mirror plate portion may be greater than or equal to a distance (h1) between the other end of the swing bearing and the end surface of the swing wrap.

At one end of the inner circumferential surface of the rotary shaft coupling part, a coupling end protruding in a radial direction is provided to contact one end of the swing bearing and support the swing bearing.

Preferably, the orbiting scroll may be made of Al.

In addition, in order to solve the above other problems, the casing; a fixed scroll installed inside the casing and provided with a fixed wrap and a sub bearing hole; an orbiting scroll having an orbiting wrap that rotates with respect to the fixed scroll and engages with the stationary wrap to form a compression chamber; And a rotational shaft disposed in one direction inside the casing, installed on the inner circumference of the sub shaft hole and the orbiting scroll, and transmitting rotational force to enable rotation of the orbiting scroll, wherein the rotation shaft is connected to the sub shaft hole. A fixed bearing is inserted and supported in a radial direction, and a swing bearing is inserted between the inner circumference of the orbiting scroll and the outer circumference of the rotation shaft to enable the orbiting scroll to rotate, and one end of the orbiting bearing is It is inserted into the inner circumference of the orbiting scroll so as to be disposed at a portion of the predetermined width of the orbiting mirror plate.

According to an example related to the present invention, the width of the part where the swing bearing is inserted among the predetermined widths of the swing mirror plate is h, the height of the swing bearing is H, and h/H has a value between 0.1 and 0.3. can

According to another example related to the present invention, the width of the part where the swing bearing is inserted among the predetermined widths of the swinging mirror plate is h, the predetermined width of the swinging mirror plate is W, and h/W is between 0.2 and 0.4. can have a value of

According to another example related to the present invention, the width of the part where the swing bearing is inserted among the predetermined widths of the swing mirror plate part is h, the distance between the other end of the swing bearing and the end surface of the swing wrap is h1, , h>h1.

In addition, the orbiting scroll may be provided with a rotational shaft coupling portion formed to pass through the orbiting wrap along an arrangement direction of the rotational shaft and accommodating the rotational bearing so as to be inserted therein.

In addition, the rotary shaft coupling portion may include a coupling side portion that contacts an outer circumference of the swing bearing to support the swing bearing.

The rotary shaft coupling part may further include a coupling end supporting the swing bearing by being in contact with one end of the swing bearing.

Preferably, the orbiting scroll may be made of Al.

In the scroll compressor of the present invention, one end of the swing bearing is inserted into the inner circumference of the orbiting scroll so that it is disposed at a portion of the predetermined width of the orbiting head plate portion, so that the center of gravity of the orbiting bearing is lower than the compression chamber. Tilting occurrence can be reduced.

In addition, in the scroll compressor of the present invention, one end of the orbiting bearing is inserted into the inner circumference of the orbiting scroll so as to be disposed at a portion of the predetermined width of the orbiting head plate, so that the occurrence of deformation on the inner circumference of the orbiting head plate is also reduced.

In addition, the scroll compressor of the present invention can alleviate the tilting phenomenon of the orbiting scroll by minimizing the height difference between the center of pressure in the compression chamber and the support point of the orbiting bearing supporting it.

In addition, in the scroll compressor of the present invention, one end of the orbiting bearing is disposed so as to overlap the orbiting head plate, so that deformation or damage to the orbiting wrap portion of the orbiting scroll can be suppressed.

1 is a cross-sectional view showing a scroll compressor of the present invention.
Figure 2 is a cross-sectional view showing a compression unit in the scroll compressor of the present invention.
Fig. 3 is a perspective view showing an example in which a swing bearing is inserted into a swing scroll;
Figure 4 is an enlarged cross-sectional view of a part of Figure 3;
5 is a plan view of FIG. 3 viewed from above;
6 is an enlarged view of a portion of FIG. 5;
7 is a conceptual diagram illustrating a position for measuring roundness in a orbiting scroll in which a swing bearing is inserted;
Fig. 8A is a conceptual diagram showing roundness at 1 position in Fig. 4;
Fig. 8B is a conceptual diagram showing roundness at 2 positions in Fig. 4;
Fig. 8c is a conceptual diagram showing roundness at position 3 in Fig. 4;
Fig. 8d is a conceptual diagram showing roundness at position 4 in Fig. 4;
9A is a conceptual diagram illustrating an example in which a load is transmitted to a swing bearing and a rotation shaft coupling portion by power transmitted from a rotation shaft;
9B is a conceptual diagram illustrating an example in which an upper portion of a swing bearing and a rotation shaft coupling portion is deformed outward by power transmitted from the rotation shaft;
9C is a conceptual diagram illustrating an example in which an intermediate portion of a swing bearing and a rotation shaft coupling portion is deformed outward by power transmitted from the rotation shaft;
Fig. 10 is a graph showing the amount of deformation in the radial direction in the scroll compressors of examination specifications 1 to 4, mass production, and the present invention.
11 is a table showing a material, a width (h) of a portion where a swing bearing is inserted, a height (H) of the swing bearing, and a height of the swing head part among predetermined widths of the swing head plate;
12 is a table showing the oil film thickness of the bearing of the fixed scroll according to the position of the orbiting bearing of the orbiting scroll.

Hereinafter, the scroll compressor 10 according to the present invention will be described in detail based on the accompanying drawings. In the following description, descriptions of some components may be omitted to clarify the characteristics of the present invention.

In addition, "upper side" used in the following description means the direction away from the support surface supporting the scroll compressor 10 according to the embodiment of the present invention, that is, the upper side of the rolling part when viewed from the center of the rolling part and the compression part. . "Lower side" means a direction closer to the support surface, that is, the lower side of the compression part when viewed from the center of the transmission part and the compression part.

In addition, the term "axial direction" used in the following description means the longitudinal direction of the rotating shaft 125. “Axial direction” can be understood as an up-and-down direction. “Radial direction” means a direction intersecting the axis of rotation 125 .

In addition, in the following description, the vertical scroll compressor 10 in which the transmission part and the compression part are arranged in the vertical axis direction, and the lower compression type scroll compressor 10 in which the compression part is located below the transmission part will be described as an example.

In addition, the high-pressure type scroll compressor 10 in which the refrigerant intake pipe forming the suction passage is directly connected to the compression unit and the refrigerant discharge pipe 116 communicates with the inner space of the casing 110 will be described as an example.

1 is a cross-sectional view showing a scroll compressor 10 of the present invention, and FIG. 2 is a cross-sectional view showing a compression unit in the scroll compressor 10 of the present invention.

The scroll compressor (10) of the present invention includes a casing (110), a fixed scroll (140), an orbiting scroll (150) and a rotating shaft (125).

The fixed scroll 140 is installed inside the casing 110 and is provided with a fixed wrap 144. The fixed scroll 140 may further include a sub bearing hole 1431.

The orbiting scroll 150 rotates with respect to the fixed scroll 140 and is connected to the orbiting wrap 152 engaged with the stationary wrap 144 to form a compression chamber at one end of the orbiting wrap 152. A turning mirror plate portion 151 formed with a predetermined width is provided.

The rotating shaft 125 is disposed in one direction inside the casing 110 and is installed on the inner circumference of the fixed scroll 140 and the orbiting scroll 150 to transmit rotational force to enable the orbiting scroll 150 to rotate let it

Between the inner circumference of the orbiting scroll 150 and the outer circumference of the rotary shaft 125, a orbiting bearing 173 supporting the orbiting scroll 150 to enable orbital rotation is inserted. In addition, one end of the swing bearing 173 is inserted into the inner circumference of the orbiting scroll 150 so as to be disposed at a portion of a predetermined width of the orbiting mirror plate 151 .

In the present invention, one end of the swing bearing 173 prevents deformation or damage in the vicinity of the orbiting mirror plate unit 151 of the orbiting scroll 150 by adjusting the overlapping depth of the orbiting mirror plate unit 151 having a predetermined width. can do

When one end of the swing bearing 173 is disposed in the entirety of the predetermined width of the swing head plate 151, the center of gravity of the swing bearing 173 is relatively lower than the compression chamber, so the swing scroll A tilting phenomenon occurs while the 150 rotates.

Conversely, when one end of the swing bearing 173 is not disposed within the predetermined width of the swing mirror plate portion 151, deformation occurs on the inner circumference of the swing mirror plate portion 151 where the swing bearing 173 is not disposed. occurs

That is, one end of the swing bearing 173 is inserted into the inner circumference of the orbiting scroll 150 so as to be disposed at a portion of the predetermined width of the orbiting mirror plate unit 151, so that the center of gravity of the orbiting bearing 173 is lower than the compression chamber. Since it is prevented from being located at the bottom, the occurrence of tilting is reduced, and also, the occurrence of deformation in the inner circumference of the turning head plate portion 151 is also reduced.

On the other hand, in the scroll compressor 10 of the present invention, the orbiting scroll 150 may be made of Al (aluminum) material, compared to the existing cast iron material, due to the reduced weight, the rotation of the orbiting scroll 150 The centrifugal force is reduced, and the compression efficiency is increased by the high-speed operation.

However, reliability and efficiency are lowered at the “specific position of the orbiting scroll 150”, and the present invention, by the arrangement structure of the orbiting scroll 150 and the orbiting bearing 173 described later, “of the orbiting scroll 150 It is intended to solve these problems of deteriorating reliability and efficiency in “specific locations”.

A more detailed structure in which the orbiting bearing 173 is installed on the inner circumference of the orbiting scroll 150 and the orbiting mirror plate 151 to enable this will be described later.

Referring to FIG. 1, a high-pressure, lower-compression type scroll compressor 10 (hereinafter, abbreviated as scroll compressor 10) according to the present embodiment is a drive motor constituting a transmission part in the upper half of a casing 110. 120 is installed, and the main frame 130, the fixed scroll 140, the orbiting scroll 150, and the discharge cover 160 are sequentially installed below the drive motor 120. The normal drive motor 120 forms a transmission part, and the main frame 130, the fixed scroll 140, the orbiting scroll 150, and the discharge cover 160 form a compression part.

The transmission part is coupled to the upper end of the rotary shaft 125 to be described later, and the compression part is coupled to the lower end of the rotary shaft 125. Accordingly, the compressor has the lower compression type structure described above, and the compression unit is connected to the transmission unit by the rotating shaft 125 and operated by the rotational force of the transmission unit.

Referring to FIG. 1 , a casing 110 according to the present embodiment may include a cylindrical shell 111 , an upper shell 112 , and a lower shell 113 . The cylindrical shell 111 may have a cylindrical shape with both upper and lower ends open, the upper shell 112 may be coupled to cover the open top of the cylindrical shell 111, and the lower shell 113 may have a cylindrical shell 111 ) can be combined to cover the lower end of the opening.

Accordingly, the inner space 110a of the casing 110 is sealed, and the inner space 110a of the sealed casing 110 is divided into a lower space S1 and an upper space S2 based on the driving motor 120. Separated.

The lower space S1 is a space formed below the driving motor 120, and the lower space S1 may be divided into a storage space S11 and a discharge space S12 based on the compression unit.

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

The upper space S2 is a space formed above the drive motor 120 and forms an oil separation space in which oil is separated from the refrigerant discharged from the compression unit. The refrigerant discharge pipe 116 communicates with the upper space S2.

Inside the cylindrical shell 111, the aforementioned drive motor 120 and main frame 130 are inserted and fixed. Oil return passages Po1 and Po2 spaced apart from the inner circumferential surface of the cylindrical shell 111 by a predetermined distance may be formed on the outer circumferential surface of the driving motor 120 and the outer circumferential surface of the main frame 130 . This will be described later together with the oil return passage.

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 constituting the casing 110 in the radial direction and is coupled.

The refrigerant suction pipe 115 is formed in an L shape, and one end passes through the cylindrical shell 111 to directly communicate with the suction port 1421 of the fixed scroll 140 forming the compression part. Accordingly, the refrigerant may be introduced into the compression chamber (V) through the refrigerant suction pipe (115).

In addition, the other end of the refrigerant suction pipe 115 is connected to an accumulator (not shown) forming a suction passage outside the cylindrical shell 111 . An accumulator (not shown) is connected to the outlet side of the evaporator (not shown) through a refrigerant pipe. Accordingly, the refrigerant moving from the evaporator (not shown) to the accumulator (not shown) is directly sucked into the compression chamber (V) through the refrigerant suction pipe 115 after the liquid refrigerant is separated from the accumulator (not shown). do.

A terminal bracket (not shown) is coupled to the upper half of the cylindrical shell 111 or the upper shell 112, and a terminal (not shown) for transmitting external power to the drive motor 120 may be penetrated and coupled to the terminal bracket. .

In the upper part of the upper shell 112, the inner end 116a of the refrigerant discharge pipe 116 is formed in the inner space 110a of the casing 110, specifically, the upper space S2 formed above the drive motor 120. are coupled so that they are in communication.

The refrigerant discharge pipe 116 corresponds to a passage through which the compressed refrigerant discharged from the compression unit into the inner space 110a of the casing 110 is discharged to the outside toward a condenser (not shown). The refrigerant discharge pipe 116 may be disposed on the same axis as the rotation shaft 125 to be described later. Accordingly, the venturi tube 191, which will be described later, disposed in parallel with the refrigerant discharge tube 116 may be disposed eccentrically with respect to the axis center of the rotation shaft 125.

An oil separator (unsigned) is installed in the refrigerant discharge pipe 116 to separate oil from the refrigerant discharged from the compressor 10 to the condenser, or the refrigerant discharged from the compressor 10 flows back to the compressor 10. A check valve (unsigned) may be installed to block it.

One end of an oil circulation pipe (not shown) may be penetrated through the lower half of the lower shell 113 in the radial direction. Both ends of the oil circulation pipe are open, and the other end of the oil circulation pipe may be penetrated through the refrigerant suction pipe (115). An oil circulation valve (not shown) may be installed in the middle of the oil circulation pipe.

The oil circulation valve may be opened or closed according to the amount of oil stored in the oil storage space (S11) or according to set conditions. For example, in the early stage of operation of the compressor, the oil circulation valve is opened to allow the oil stored in the oil storage space to be circulated to the compression unit through the suction refrigerant pipe. that can be prevented

Hereinafter, referring to FIG. 1, the drive motor 120 constituting the transmission unit will be described. The drive motor 120 according to this embodiment includes a stator 121 and a rotor 122 . The stator 121 is inserted into and fixed to the inner circumferential 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 circumferential surface of the cylindrical shell 111 by hot press fitting.

A rotor accommodating portion 1211a is formed at the central portion of the stator core 1211 through which the rotor 122 is rotatably inserted. A plurality of stator-side oil return grooves 1211b cut or recessed in a D-cut shape along the axial direction may be formed on the outer circumferential surface of the stator core 1211 at predetermined intervals along the circumferential direction.

A plurality of teeth (not shown) and slots (not shown) are alternately formed on the inner circumferential surface of the rotor accommodating portion 1211a in a circumferential direction, and a stator coil 1212 is wound around each tooth through both slots.

More precisely, a slot may be a space between neighboring stator coils in the circumferential direction. In addition, the slot forms an internal passage 120a, an air gap passage 120b is formed between the inner circumferential surface of the stator core 1211 and the outer circumferential surface of the rotor core 1221 to be described later, and the oil return groove 1211d is formed on the outside. A passage 120c is formed. The inner passage 120a and the air gap passage 120b form a passage through which the refrigerant discharged from the compression unit moves to the upper space S2, and the outer passage 120c is an oil storage space separated from the upper space S2. (S11) to form a first oil return passage (Po1) to be recovered.

The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source through a terminal (not shown) coupled through the casing 110 . An insulator 1213 as an insulating member is inserted between the stator core 1211 and the stator coil 1212 .

The insulator 1213 may be provided on the outer circumferential side and the inner circumferential side to accommodate the bundle of stator coils 1212 in the radial direction and extend in both axial directions of the stator core 1211 .

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

The rotor core 1221 is formed in a cylindrical shape and is accommodated in the rotor accommodating portion 1211a formed in the center of the stator core 1211 .

Specifically, the rotor core 1221 is rotatably inserted into the rotor accommodating portion 1211a of the stator core 1211 at a predetermined gap 120a. The permanent magnets 1222 are embedded in the rotor core 1221 at predetermined intervals along the circumferential direction.

A balance weight 123 may be coupled to a lower end of the rotor core 1221 . However, the balance weight 123 may be coupled to the main shaft portion 1251 of the rotating shaft 125 to be described later. This embodiment will be described based on an example in which the balance weight 123 is coupled to the rotation shaft 125. The balance weight 123 is installed on the lower and upper ends of the rotor, respectively, and the two are installed symmetrically with each other.

A rotating shaft 125 is coupled to the center of the rotor core 1221 . The upper end of the rotating shaft 125 is press-fitted and coupled to the rotor 122, and the lower end of the rotating shaft 125 is rotatably inserted into the main frame 130 and supported in the radial direction.

The main frame 130 is provided with a main bearing 171 made of a bush bearing to support the lower end of the rotating shaft 125 . Accordingly, the portion inserted into the main frame 130 among the lower ends of the rotating shaft 125 can be smoothly rotated inside the main frame 130 .

The rotating shaft 125 transfers the rotational force of the driving motor 120 to the orbiting scroll 150 constituting the compression part. As a result, the orbiting scroll 150 eccentrically coupled to the rotational shaft 125 rotates with respect to the fixed scroll 140.

Referring to FIG. 1 , a rotating shaft 125 according to the present embodiment includes a main shaft portion 1251, a first bearing portion 1252, a fixed bearing portion 1253, and an eccentric portion 1254.

The main shaft portion 1251 is an upper portion of the rotating shaft 125 and is formed in a cylindrical shape. The main shaft portion 1251 may be partially press-fitted and coupled to the rotor core 1221 .

The first bearing part 1252 is a part extending from the lower end of the main shaft part 1251 . The first bearing part 1252 may be inserted into the main bearing hole 1331 of the main frame 130 and supported in the radial direction.

The fixed bearing part 1253 means a lower part of the rotational shaft 125 . The fixed bearing part 1253 may be inserted into the sub bearing hole 1431 of the fixed scroll 140 and supported in the radial direction. The central axis of the fixed bearing part 1253 and the central axis of the first bearing part 1252 may be arranged on the same line. That is, the first bearing part 1252 and the fixed bearing part 1253 may have the same central axis.

The eccentric portion 1254 is formed between the lower end of the first bearing part 1252 and the upper end of the fixed bearing part 1253 . The eccentric portion 1254 may be inserted into and coupled to the rotating shaft coupling portion 153 of the orbiting scroll 150 to be described later.

The eccentric portion 1254 may be formed to be eccentric in a radial direction with respect to the first bearing portion 1252 and the fixed bearing portion 1253 . That is, the central axis of the eccentric part 1254 may be formed eccentrically with respect to the central axis of the first bearing part 1252 and the central axis of the fixed bearing part 1253 . Accordingly, when the rotary shaft 125 rotates, the orbiting scroll 150 can perform a orbital motion with respect to the fixed scroll 140.

Meanwhile, an oil supply passage 126 for supplying oil to the first bearing part 1252, the fixed bearing part 1253, and the eccentric part 1254 is formed in a hollow shape inside the rotating shaft 125. The oil supply passage 126 includes an internal oil passage 1261 formed along the axial direction inside the rotating shaft 125 .

The internal oil passage 1261 is a groove from the lower end of the rotary shaft 125 to a position higher than the lower end or middle height of the stator 121 or the upper end of the first bearing part 1252 as the compression part is located lower than the rolling part. It can be formed by digging. However, in an embodiment not shown, the internal oil passage 1261 may be formed by penetrating the rotating shaft 125 in the axial direction.

An oil pickup 127 for pumping oil filled in the oil storage space S11 may be coupled to a lower end of the rotary shaft 125, that is, a lower end of the fixed bearing part 1253. The oil pickup 127 is composed of an oil supply pipe 1271 inserted into and coupled to the internal oil passage 1261 of the rotary shaft 125, and a blocking member 1272 for receiving the oil supply pipe 1271 to block the entry of foreign substances. can The oil supply pipe 1271 may pass through the discharge cover 160 and extend downward to be submerged in oil in the storage space S11.

The rotary shaft 125 is communicated with the internal oil passage 1261, and the oil moving upward along the internal oil passage 1261 is directed to the first bearing part 1252, the fixed bearing part 1253, and the eccentric part 1254. A plurality of oil supply holes may be formed to guide.

1 and 2, the compression unit according to the present embodiment includes a main frame 130, a fixed scroll 140, an orbiting scroll 150, a discharge cover 160, and a flow guide 180 (FIG. 1). do.

The main frame 130 includes a frame head plate portion 131, a frame side wall portion 132, and a main bearing accommodating portion 133.

The frame head plate 131 is formed in an annular shape and is installed below the driving motor 120 . The frame side wall portion 132 extends in a cylindrical shape from the lower edge of the frame head plate portion 131, and the outer circumferential surface of the frame side wall portion 132 is fixed to the inner circumferential surface of the cylindrical shell 111 by hot press or by welding. . Accordingly, the storage space (S11) and the discharge space (S12) constituting the lower space (S1) of the casing (110) are separated by the frame head plate portion (131) and the frame side wall portion (132).

A frame discharge hole (hereinafter referred to as a second discharge hole) 1321 forming a part of the discharge passage may be formed to pass through the frame side wall portion 132 in an axial direction. The second discharge hole 1321 is formed to correspond to the scroll discharge hole (first discharge hole) 1422 of the fixed scroll 140 to be described later, and together with the first discharge hole 1422 forms a refrigerant discharge passage (unsigned). will achieve

The second discharge hole 1321 may be formed long in the circumferential direction or formed in plural at predetermined intervals along the circumferential direction. Accordingly, the second discharge hole 1321 secures a discharge area while maintaining a minimum radial width to secure a volume of the compression chamber compared to the same diameter of the main frame 130 . The first discharge hole 1422 provided in the fixed scroll 140 and forming a part of the discharge passage may be formed in the same way.

A discharge guide groove 1322 accommodating a plurality of second discharge holes 1321 may be formed at an upper end of the second discharge hole 1321, that is, on an upper surface of the frame head plate portion 131. At least one discharge guide groove 1322 may be formed according to the formation position of the second discharge hole 1321 . For example, when the second discharge holes 1321 are made of three groups, the discharge guide grooves 1322 include three discharge guide grooves 1322 to accommodate the second discharge holes 1321 of three groups, respectively. can be formed as The three discharge guide grooves 1322 may be formed to be positioned on the same line in the circumferential direction.

The discharge guide groove 1322 may be formed wider than the second discharge hole 1321 . For example, the second discharge hole 1321 may be formed on the same line in the circumferential direction as the first oil return groove 1323 to be described later. Therefore, when the flow guide 180 to be described later is provided, it is difficult to locate the second discharge hole 1321 having a small cross-sectional area inside the flow guide 180. Accordingly, a discharge guide groove 1322 is formed at the end of the second discharge hole 1321, and the inner circumferential side of the discharge guide groove 1322 may radially extend to the inside of the flow guide 180.

Through this, the inner diameter of the second discharge hole 1321 is made small, so that the second discharge hole 1321 is formed near the outer circumferential surface of the frame 130 while the second discharge hole 1321 is formed in the flow path by the flow guide 180. It may be prevented from being rejected toward the outside of the guide 180, that is, toward the outer circumferential surface of the stator 121.

The outer circumferential surface of the frame head plate portion 131 and the outer circumferential surface of the frame side wall portion 132 forming the outer circumferential surface of the main frame 130 include frame oil recovery grooves (hereinafter referred to as first oil recovery grooves) forming part of the second oil return passage Po2. A groove) 1323 may be formed through in the axial direction. Only one first oil return groove 1323 may be formed, or may be formed at predetermined intervals in the circumferential direction along the outer circumferential surface of the main frame 130 . Accordingly, the discharge space (S12) of the casing 110 communicates with the oil storage space (S11) of the casing 110 through the first oil return groove (1323).

The first oil return groove 1323 is formed to correspond to the scroll oil return groove (hereinafter referred to as the second oil return groove) 1423 of the fixed scroll 140 to be described later, and is formed to correspond to the second oil return groove of the fixed scroll 140. Together with 1423, a second oil return passage is formed.

The main bearing accommodating portion 133 protrudes upward toward the drive motor 120 from the upper surface of the central portion of the frame neck plate portion 131 . The main bearing accommodating portion 133 is formed by penetrating the main bearing hole 1331 having a cylindrical shape in the axial direction, and the first bearing part 1252 of the rotating shaft 125 is inserted into the main bearing hole 1331 to give a radial radius. supported in the direction

Hereinafter, the fixed scroll 140 will be described with reference to FIGS. 1 and 2. The fixed scroll 140 according to the present embodiment includes a fixed head portion 141, a fixed side wall portion 142, and a sub-bearing portion 143. ) and a fixed wrap 144.

The fixed head plate portion 141 is formed in a disk shape with a plurality of concave portions formed on the outer circumferential surface, and a sub bearing hole 1431 constituting the sub bearing portion 143 to be described later may be formed through the center in the vertical direction. Discharge ports 1411 and 1412 may be formed around the sub shaft hole 1431 to communicate with the discharge pressure chamber Vd and discharge the compressed refrigerant into the discharge space S12 of the discharge cover 160 to be described later.

Although not shown in the drawings, only one discharge port may be formed so as to communicate with both the first compression chamber V1 and the second compression chamber V2 to be described later. However, as in this embodiment, the first discharge port (unsigned) may be communicated with the first compression chamber (V1), and the second discharge port (unsigned) may be communicated with the second compression chamber (V2). Accordingly, the refrigerant compressed in the first compression chamber V1 and the second compression chamber V2 may be independently discharged through different discharge ports.

The fixed side wall portion 142 may be formed in an annular shape by extending vertically from the edge of the upper surface of the fixed end plate portion 141 . The fixed side wall portion 142 may be coupled to the frame side wall portion 132 of the main frame 130 so as to face each other in the vertical direction.

A scroll discharge hole (hereinafter referred to as a first discharge hole) 1422 is formed through the fixed side wall portion 142 in an axial direction. The first discharge hole 1422 may be formed long in the circumferential direction or may be formed in a plurality at predetermined intervals along the circumferential direction. Accordingly, the first discharge hole 1422 secures a discharge area while maintaining a minimum radial width, thereby securing a compression chamber volume compared to the same diameter of the fixed scroll 140.

The first discharge hole 1422 communicates with the previously described second discharge hole 1321 in a state in which the fixed scroll 140 is coupled to the cylindrical shell 111. Accordingly, the first discharge hole 1422 together with the previously described second discharge hole 1321 forms a refrigerant discharge passage.

A second oil recovery groove 1423 may be formed on an outer circumferential surface of the fixed side wall portion 142 . The second oil return groove 1423 is in communication with the first oil return groove 1323 provided in the main frame 130, and the oil recovered through the first oil return groove 1323 is transferred to the oil storage space S11. will guide Accordingly, the first oil return groove 1323 and the second oil return groove 1423 together with the oil return groove 1612 of the discharge cover 160 to be described later form a second oil return passage Po2.

A suction port 1421 penetrating the fixed side wall portion 142 in a radial direction is formed in the fixed side wall portion 142 . The end of the refrigerant suction pipe 115 penetrating the cylindrical shell 111 is inserted into the suction port 1421 and coupled thereto. Accordingly, the refrigerant may flow into the compression chamber V through the refrigerant suction pipe 115 .

The sub-bearing part 143 extends from the center of the fixed end plate part 141 toward the discharge cover 160 in the axial direction. A cylindrical sub-bearing hole 1431 is formed through the center of the sub-bearing part 143 in the axial direction, and the fixed bearing part 1253 of the rotary shaft 125 is inserted into the sub-bearing hole 1431 to rotate in the radial direction. can be supported Accordingly, the lower end (or fixed bearing part) of the rotary shaft 125 is inserted into the sub-bearing part 143 of the fixed scroll 140 and supported in the radial direction, and the eccentric part 1254 of the rotary shaft 125 is the sub-bearing part It may be supported in the axial direction on the upper surface of the fixed head plate portion 141 forming the periphery of (143).

The fixed wrap 144 may extend from the upper surface of the fixed end plate 141 toward the orbiting scroll 150 in the axial direction. The stationary wrap 144 is engaged with the orbiting wrap 152 to be described later to form a compression chamber V. The fixed wrap 144 will be described later along with the orbiting wrap 152.

Hereinafter, the orbiting scroll 150 will be described with reference to FIGS. 1 and 2. The orbiting scroll 150 according to the present embodiment includes an orbiting mirror plate part 151, an orbiting wrap 152, and a rotating shaft coupling part 153.

The turning mirror plate unit 151 is formed in a disk shape and accommodated in the main frame 130 . The upper surface of the revolving head plate unit 151 may be supported in the axial direction by the main frame 130 with a back pressure sealing member (not shown) interposed therebetween.

The orbiting wrap 152 may extend toward the fixed scroll 140 from the lower surface of the orbiting mirror plate 151 . The orbiting wrap 152 is engaged with the stationary wrap 144 to form the compression chamber V.

The orbiting wrap 152 may be formed in an involute shape together with the stationary wrap 144 . However, the orbiting wrap 152 and the stationary wrap 144 may be formed in various shapes other than involute.

For example, the orbiting wrap 152 has a shape in which a plurality of circular arcs having different diameters and origins are connected, and the outermost curve may be formed in a substantially elliptical shape having a major axis and a minor axis. This fixing wrap 144 can also be formed in the same way.

An inner end of the orbiting wrap 152 is formed at a central portion of the orbiting mirror plate portion 151, and a rotation shaft coupling portion 153 may be axially formed through the central portion of the orbiting mirror plate portion 151.

The eccentric part 1254 of the rotation shaft 125 is rotatably inserted and coupled to the rotation shaft coupling part 153 . Accordingly, the outer periphery of the rotating shaft coupling part 153 is connected to the orbiting wrap 152 to serve to form the compression chamber V together with the fixed wrap 144 during the compression process.

The rotating shaft coupling part 153 may be formed to overlap the height of the orbiting wrap 152 on the same plane. That is, the rotating shaft coupling part 153 may be disposed at a height where the eccentric part 1254 of the rotating shaft 125 overlaps the orbiting wrap 152 on the same plane. Accordingly, the repulsive force and the compressive force of the refrigerant are applied to the same plane based on the orbiting head plate portion 151 and cancel each other out, and through this, the inclination of the orbiting scroll 150 due to the action of the compressive force and the repulsive force can be suppressed. .

The rotary shaft coupling part 153 may include an engaging side part 153a that contacts the outer circumference of the swing bearing 173 and supports the swing bearing 173 .

In addition, the rotary shaft coupling part 153 may further include a coupling end 153b that contacts one end of the swing bearing 173 and supports the swing bearing 173 .

Referring to FIG. 4 , an engaging side portion 153a formed vertically on the inner circumference of the rotary shaft coupling portion 153 to contact the outer circumference of the swing bearing 173 is shown, and is in contact with the upper end of the swing bearing 173 to the swing bearing. A coupling end 153b supporting 173 is shown.

On the other hand, the compression chamber (V) is formed in a space composed of the fixed head plate portion 141 and the fixed wrap 144, and the orbiting head plate portion 151 and the orbiting wrap 152. In addition, the compression chamber V includes a first compression chamber V1 formed between the inner surface of the fixed wrap 144 and the outer surface of the orbiting wrap 152 based on the fixed wrap 144, and the fixed wrap ( 144) and the inner surface of the orbiting wrap 152 may be formed of a second compression chamber (V2).

Hereinafter, the discharge cover 160 will be described with reference to FIGS. 1 and 2 . The discharge cover 160 includes a cover housing part 161 and a cover flange part 162 .

The cover housing part 161 forms a cover space part 1611 forming the discharge space S3 together with the lower surface of the fixed scroll 140 therein.

The outer circumferential surface of the cover housing 161 is in close contact with the inner circumferential surface of the casing 110, but is partially spaced apart along the circumferential direction to form an oil return groove 1612. The oil return groove 1612 forms a third oil return groove in the oil return groove 1621 provided on the outer circumferential surface of the cover flange portion 162, and the third oil return groove of the discharge cover 160 is the main frame described above. The second oil return passage (Po2) is formed together with the first oil return groove of (130) and the second oil return groove of the fixed scroll (140).

At least one discharge hole receiving groove 1613 may be formed on the inner circumferential surface of the cover housing part 161 along the circumferential direction. The discharge hole receiving groove 1613 is formed to be depressed radially outward, and the first discharge hole 1422 of the fixed scroll 140 constituting the discharge passage is located inside the discharge hole receiving groove 1613. can be formed Accordingly, the inner surface of the cover housing 161, excluding the discharge hole receiving groove 1613, adheres to the outer circumferential surface of the fixed scroll 140, that is, the outer circumferential surface of the fixed head plate 141 to form a kind of sealing part.

The total circumferential angle of the discharge hole receiving groove 1613 may be smaller than or equal to the total circumferential angle of the inner circumferential surface of the discharge space S3 excluding the discharge hole receiving groove 1613 . Accordingly, a sufficient sealing area can be secured on the inner circumferential surface of the discharge space S3 excluding the discharge hole receiving groove 1613, and a length in the circumferential direction at which the cover flange portion 162 can be formed can be secured. .

The cover flange portion 162 may be formed to extend radially from an outer circumferential surface of a portion constituting the sealing portion, that is, a portion of the top surface of the cover housing portion 161 excluding the discharge hole receiving groove 1613 .

A fastening hole (unsigned) for fastening the discharge cover 160 to the fixed scroll 140 with bolts is formed in the cover flange part 162, and a plurality of fastening holes are spaced at predetermined intervals along the circumferential direction. The oil return groove 1621 may be formed to be recessed in the radial direction. This oil return groove forms a third oil return groove together with the oil return groove 1612 of the cover housing 161 described above.

Next, Euroguide will be explained.

Referring to Figures 2 and 3, the flow guide 180 according to this embodiment is installed between the transmission unit and the compression unit, for example, in the discharge space (S12). Specifically, the flow guide 180 may be provided at the upper end of the main frame 130 facing the lower end of the drive motor 120 .

The passage guide 180 separates the discharge space S12 into a refrigerant discharge passage and an oil return passage. Accordingly, the refrigerant discharged from the compression unit to the discharge space (S12) moves to the upper space (S2) through the inner passage (120a) and the air gap passage (120b), and the oil separated from the refrigerant in the upper space (S2) It can be recovered to the storage space (S11) through the external passage (120c).

The flow guide 180 may be formed in one annular shape or may be formed in a plurality of circular arc shapes. Hereinafter, an example in which the flow guide 180 is formed in an annular shape will be mainly described, but even when formed in a plurality of circular arc shapes, the basic configuration for separating the refrigerant and the oil and the effect thereof are similar.

For example, the flow guide 180 may include a bottom portion 181 , an outer wall portion 182 , and an inner wall portion 183 .

The bottom part 181 is formed in an annular shape and fixed to the upper surface of the main frame 130 . A discharge passage cover 1811 extends radially on the outer circumferential surface of the bottom portion 181, and a discharge passage 1812 overlaps with the discharge guide groove 1322 of the main frame 130 in the discharge passage cover 1811. this can penetrate.

The outer wall portion 182 extends toward the insulator 1213 from approximately the outer circumferential surface of the bottom portion 181 . The outer wall portion 182 may be inserted inside or outside the insulator 1213 to overlap with the insulator 1213 . The outer wall portion 182 may be formed in an annular shape extending in the circumferential direction or may be formed in an arc shape.

When the outer wall portion 182 is formed in an annular shape, the diameter of the outer wall portion 182 may be smaller or larger than the diameter of the insulator 1213, or the upper end of the outer wall portion may be spaced apart from the lower end of the insulator 1213. It can be. Accordingly, a gap is generated between the outer wall portion 182 and the insulator 1213, and the refrigerant (liquid refrigerant) discharged to the inside of the outer wall portion 182 passes through the second end 192b of the liquid refrigerant discharge pipe 192 to be described later. The liquid refrigerant can be quickly discharged to the outside of the compressor through the liquid refrigerant discharge unit 190.

Although not shown in the drawings, when a communication path such as a gap is not formed between the annular outer wall portion 182 and the insulator 1213, the inner space is formed on the bottom portion 181 or the upper surface of the main frame 130 facing it. A communication groove (not shown) may be formed to communicate S12a and the outer space S12b.

The inner wall portion 183 extends toward the insulator 1213 from approximately the inner circumferential surface of the bottom portion 181 . The inner wall portion 183 may extend in the axial direction, or may be bent and extended so as to surround the balance weight 123 as shown in the drawing.

FIG. 3 is a perspective view showing an example in which the turning bearing 173 is inserted into the turning scroll 150, FIG. 4 is an enlarged cross-sectional view of part A-A' in FIG. 3, and FIG. 5 is a plan view of FIG. 3 viewed from the top. 6 is an enlarged view of part B of FIG. 5 .

Hereinafter, with reference to FIGS. 3 to 6, the scroll compressor 10 of the present invention will be described in more detail.

As described above, the scroll compressor 10 of the present invention includes a casing 110, a fixed scroll 140, an orbiting scroll 150 and a rotating shaft 125.

The fixed scroll 140 is installed inside the casing 110 and is provided with a fixed wrap 144.

The orbiting scroll 150 rotates with respect to the fixed scroll 140 and is connected to the orbiting wrap 152 engaged with the stationary wrap 144 to form a compression chamber at one end of the orbiting wrap 152. A turning mirror plate portion 151 formed with a predetermined width is provided.

The rotating shaft 125 is disposed in one direction inside the casing 110 and is installed on the inner circumference of the fixed scroll 140 and the orbiting scroll 150 to transmit rotational force to enable the orbiting scroll 150 to rotate let it

Between the inner circumference of the orbiting scroll 150 and the outer circumference of the rotary shaft 125, a orbiting bearing 173 supporting the orbiting scroll 150 to enable orbital rotation is inserted. In addition, one end of the swing bearing 173 is inserted into the inner circumference of the orbiting scroll 150 so as to be disposed at a portion of a predetermined width of the orbiting mirror plate 151 .

When one end of the swing bearing 173 is disposed in the entirety of the predetermined width of the swing head plate 151, the center of gravity of the swing bearing 173 is relatively lower than the compression chamber, so the swing scroll A tilting phenomenon occurs while the 150 rotates.

Conversely, when one end of the swing bearing 173 is not disposed within the predetermined width of the swing mirror plate portion 151, deformation occurs on the inner circumference of the swing mirror plate portion 151 where the swing bearing 173 is not disposed. occurs

That is, one end of the swing bearing 173 is inserted into the inner circumference of the orbiting scroll 150 so as to be disposed at a portion of the predetermined width of the orbiting mirror plate unit 151, so that the center of gravity of the orbiting bearing 173 is lower than the compression chamber. Since it is prevented from being located at the bottom, the occurrence of tilting is reduced, and also, the occurrence of deformation in the inner circumference of the turning head plate portion 151 is also reduced.

In FIGS. 3 and 4, the orbiting scroll 150 is shown with the orbiting head plate 151 positioned below and the orbiting wrap 152 positioned upward, which corresponds to the scroll compressor 10 in FIGS. 1 and 2. It is shown opposite to the arrangement direction of the orbiting scroll 150 installed within. That is, in FIGS. 1 and 2, between the main frame and the fixed scroll 140 of the orbiting scroll 150, the orbiting mirror plate 151 is positioned at a relatively upper portion, and the orbiting wrap 152 is positioned at an upper portion. has been

FIG. 3 shows an example in which a rotating shaft 125 coupling portion formed in the arrangement direction of the rotating shaft 125 is provided inside the rotating wrap 152, and an example in which a swing bearing 173 is inserted into the rotating shaft 125 coupling portion is shown. do. Unlike FIGS. 1 and 2 in FIG. 3 , the rotation shaft 125 is not shown.

In addition, FIG. 4 shows an example in which a part of FIG. 3 is enlarged and the swing bearing 173 is press-fitted into the orbiting scroll 150.

As shown in FIG. 4 , the width of the portion where the swing bearing 173 is inserted among the predetermined widths of the swing mirror plate 151 is h, and the height of the swing bearing 173 is H. h is the length of the part where the swing bearing 173 is press-fitted in the swing mirror plate part 151, and can be understood as the length of the press-fit part, which is the part where the swing bearing 173 is press-fitted on the inner circumference of the swing head plate part 151. may be

In the present invention, h / H may have a value between 0.1 and 0.3, so that the deformation amount of the rotating shaft 125 coupling part of the orbiting scroll 150 and the orbiting bearing 173 is minimized.

Conventionally, as a orbiting scroll 150 made of GC250 material, it is used as a scroll compressor 10 for 2.0 to 3.5 hp, an example of a scroll compressor 10 (R1, 20Fr., 3.5hp) in mass production is a swing bearing 173 ) is mass-produced at the level of H = 20, h = 3, and h / H = 0.15.

As the material of the orbiting scroll 150 is changed from conventional cast iron (GC250) to Al, the horsepower is increased, and deformation occurs at the minimum thickness of the coupling part of the rotating shaft 125 where the orbiting bearing 173 is press-fitted. . After the scroll compressor 10 is operated, the swing bearing 173 is deformed at the minimum thickness position of the coupling part of the rotating shaft 125 where the swing bearing 173 is press-fitted, and as a result, a tilting phenomenon also occurs in the orbiting scroll 150 However, the tilting phenomenon can be reduced by adjusting the position of the swing bearing 173.

In addition, in FIG. 4 , the predetermined width of the turning mirror plate 151 is W. In the present invention, h / W may have a value between 0.2 and 0.4, so that the amount of deformation of the rotating shaft 125 coupled portion of the orbiting scroll 150 and the orbiting bearing 173 is minimized.

Meanwhile, in FIG. 4, the distance from the coupling end 153b to the top of the orbiting wrap 153 is shown as h1, where h1 is the distance from the top of the swing bearing 173 to the top of the orbiting wrap 153, That is, it can be understood as the height of the orbiting wrap 153 from the upper end of the orbiting bearing 173.

If the height h1 of the swing wrap 153 from the upper end of the swing bearing 173 is longer than the overlap length h at which the swing bearing 173 overlaps in the swing head plate 151, the swing bearing ( 173) is moved to the lower side, that is, toward the orbiting head plate 151, which is a factor in increasing the tilting of the orbiting scroll 150 by widening the gap between the action point 153c and the support point 173a.

The action point 153c is a point that acts toward the inner surface of the orbiting wrap in the compression chamber by the operation of the orbiting scroll, and the support point 173a is a point where the force applied to the outside from the inner circumference of the orbiting bearing 173 acts. is one point

Therefore, if the lap height h1 from the upper end of the swing bearing 173 is smaller than or equal to the overlap length h of the swing bearing 173, preferably smaller (h1<h), the orbiting scroll 150 It is possible to reduce tilting of and at the same time reduce deformation of the orbiting wrap 153.

Also shown in FIG. 4 are measurement positions 1 to 4 of roundness, which are respectively shown in FIGS. 8A to 8D . The roundness at each of positions 1 to 4 will be described with respect to FIGS. 8A to 8D.

5 shows an example in which the swing bearing 173 is installed on the inner circumference of the rotation shaft 125 coupling part of the orbiting scroll 150, and in FIG. 6, part B of FIG. 5 is enlarged, and in FIGS. 5 and 6, the minimum thickness point (d ) is also shown. While the orbiting scroll 150 orbits, deformation may occur at the minimum thickness point d. In particular, the material of the orbiting scroll 150 is changed to Al, and as a result, horse power increases and deformation occurs at the minimum thickness point (d).

FIG. 7 is a conceptual diagram showing the roundness measurement position in the orbiting scroll 150 into which the orbiting bearing 173 is inserted, FIG. 8a is a conceptual diagram showing the circularity at position 1 in FIG. 4, and FIG. 8c is a conceptual diagram showing roundness at position 3 in FIG. 4 , and FIG. 8d is a conceptual diagram showing roundness at position 4 in FIG. 4 .

Deformation at points 1 to 4 in FIG. 4 will be described with reference to FIGS. 7 to 8D.

The deformation at one point in FIG. 4 is shown in FIG. 8A, and among one point in FIG. 4, the maximum deformation is in the lower left portion where the minimum thickness point (d) in FIG. 7 is located.

The deformation at two points in FIG. 4 is shown in FIG. 8B, and among the two points in FIG. 4, the maximum deformation occurs in the lower left portion where the minimum thickness point (d) in FIG. 7 is located.

The deformation at 3 points in FIG. 4 is shown in FIG. 8C, and among the 3 points in FIG. 4, the maximum deformation is in the lower left portion where the minimum thickness point (d) in FIG. 7 is located.

It can be seen in FIG. 8d that deformation does not occur at point 4 in FIG. 4 .

Referring to FIGS. 8A to 8D , it can be seen that a lot of deformation occurs at points 1 to 3 in FIG. 4 , and no deformation occurs at point 4 in FIG. 4 .

8a to 8c, the height of the orbiting scroll 150 and the length h of the part where the orbiting bearing 173 is press-fitted in the orbiting mirror plate 151 are It can act as a big factor in deformation. Due to this, during the operation of the scroll compressor 10, the orbiting scroll 150 and the orbiting bearing 173 cause instability in behavior at positions where deformation is large (for example, points 1 to 3 in FIG. 4), and to prevent this For this purpose, it is important to select the arrangement of the orbiting scroll 150 and the orbiting bearing 173 to minimize deformation.

As described above, the arrangement of the swing bearing 173 is determined by the width (h) of the part where the swing bearing 173 is inserted among the predetermined widths of the swing mirror plate part 151 and the height of the swing bearing 173. Between (H), the swing bearing 173 should be disposed on the orbiting scroll 150 so that h/H has a value between 0.1 and 0.3.

For example, in the orbiting scroll 150 of the present invention, H may be 25, h may be 5.8, and h/H may be 0.23.

FIG. 9A shows an example in which a load is transferred to a coupling portion between the swing bearing 173 and the rotation shaft 125 by power transmitted from the rotation shaft 125 . In addition, an example in which the upper part of the swing bearing 173 and the rotation shaft 125 is deformed outward by the power transmitted from the rotation shaft 125 is shown in FIG. 9B, and the swing bearing by the power transmitted from the rotation shaft 125 An example in which the middle part of the coupling part 173 and the rotating shaft 125 is deformed outward is shown in FIG. 9C.

The graph of FIG. 10 shows the amount of deformation in the radial direction in the compressors of the review specifications 1 to 4, the currently mass-produced compressors, and the scroll compressor 10 of the present invention.

As shown in FIG. 10, the compressors of the review specifications 1 to 4 and currently mass-produced show a maximum deformation amount in the radial direction of about 12 to 19 μm.

The compressors of the review specifications 1 to 4 are the results obtained by analyzing only the peripheral shape change without moving the position of the swing bearing 173 in currently mass-produced compressors.

On the other hand, in the scroll compressor 10 of the present invention, the maximum deformation amount in the radial direction of 10 μm is shown in FIG.

11 shows the material, the width (h) of the part where the swing bearing 173 is inserted among the predetermined widths of the swing mirror plate part 151, the height (H) of the swing bearing 173, and the height of the swing mirror plate part 151. is a table showing

Referring to FIG. 11 , the width (h) of the part where the swing bearing 173 is inserted among the predetermined widths of the swing mirror plate part 151, the height (H) of the swing bearing 173, and the swing mirror plate part 151 Referring to the table shown in FIG. 11, the predetermined width (head plate) (W, FIG. 4) is in the range of (i) 0.1 < h / H < 0.3, and (ii) 0.2 < h / head (W) < 0.8 Radial deformation in the range is minimal.

12 is a table showing the oil film thickness of the bearing of the fixed scroll 140 according to the position of the orbiting bearing 173 of the orbiting scroll 150.

2 and 12 together, when the orbiting bearing 173 of the orbiting scroll 150 is moved upward, the minimum oil film thickness of the orbiting bearing 173 is increased, and in particular, the orbital bearing at low hertz (Hz) (Hz) 173) is improved. In addition, it can be confirmed that the oil film thickness of the bearing of the fixed scroll 140 increases as the swing bearing 173 goes down the swing mirror plate part 151 . When the width (thickness, W) of the swing mirror plate part 151 is 13, when the position of the swing bearing 173 fluctuates from 5.8 to 8.8, the minimum oil film increases from a minimum of 0.90 μm to 1.06 μm, An example in which the oil film thickness increases from a maximum oil film degree of 2.46 μm to 2.61 μm is shown.

In addition, when the width (thickness, W) of the swing mirror plate part 151 is 10.5, and the position of the swing bearing 173 varies from 5.8 to 8.8, the minimum oil film thickness increases from 1.14 μm to 1.32 μm. , the maximum oil film degree, an example in which the oil film thickness increases from a maximum of 2.65 μm to 2.82 μm is shown.

The scroll compressor 10 according to the present embodiment as described above operates as follows.

That is, when power is applied to the driving motor 120, rotational force is generated in the rotor 122 and the rotational shaft 125 to rotate, and the orbiting scroll 150 eccentrically coupled to the rotational shaft 125 rotates the Oldham ring 170. As a result, a turning motion is performed with respect to the fixed scroll (140).

Then, the volume of the compression chamber (V) gradually increases from the suction pressure chamber (Vs) formed outside the compression chamber (V) to the intermediate pressure chamber (Vm) formed continuously toward the center, and to the discharge pressure chamber (Vd) in the center. it gradually decreases

Then, the refrigerant moves to the condenser (not shown), the expander (not shown), and the evaporator (not shown) of the refrigeration cycle, and then moves to the accumulator (not shown), and the refrigerant is compressed through the refrigerant suction pipe 115. It moves toward the suction pressure chamber Vs constituting the chamber V.

Then, the refrigerant sucked into the suction pressure chamber (Vs) is compressed while moving to the discharge pressure chamber (Vd) through the intermediate pressure chamber (Vm) along the movement trajectory of the compression chamber (V), and the compressed refrigerant is compressed in the discharge pressure chamber (Vd). It is discharged into the discharge space (S12) of the discharge cover 160 through the discharge ports 1411 and 1412.

Then, the refrigerant discharged into the discharge space (S12) of the discharge cover 160 (the refrigerant is mixed with oil to form a mixed refrigerant. However, during the description, the mixed refrigerant or refrigerant may be mixed) is discharged from the discharge cover 160. It is moved to the discharge space (S12) formed between the main frame 130 and the drive motor 120 through the hole receiving groove 1613 and the first discharge hole 1422 of the fixed scroll 140. The mixed refrigerant passes through the driving motor 120 and moves to the upper space S2 of the casing 110 formed above the driving motor 120 .

The mixed refrigerant moved to the upper space (S2) is separated into refrigerant and oil in the upper space (S2), and the refrigerant (or some mixed refrigerant in which oil is not separated) passes through the refrigerant discharge pipe (116) to the casing (110). It is discharged to the outside and moves to the condenser of the refrigeration cycle.

On the other hand, the oil separated from the refrigerant in the upper space (S2) (or the mixed oil in which the liquid refrigerant is mixed) passes through the first oil return passage (Po1) between the inner circumferential surface of the casing 110 and the stator 121 to the lower space ( S1), and the oil moved to the lower space (S1) is a storage oil space ( It is recovered in S11).

This oil is supplied to each bearing surface (unsigned) through the oil supply passage 126, and a part is supplied to the compression chamber (V). The oil supplied to the bearing surface and the compression chamber V is discharged to the discharge cover 160 together with the refrigerant, and a series of recovery processes are repeated.

At this time, as the flow guide 180 separating the refrigerant discharge passage and the oil return passage is installed between the lower end of the drive motor 120 constituting the discharge space S12 and the upper end of the main frame 130, the discharge from the compression unit It is possible to suppress mixing of the refrigerant moving to the upper space (S2) and the oil moving from the upper space (S2) to the lower space (S1).

Meanwhile, one end of the swing bearing 173 is inserted into the inner circumference of the orbiting scroll 150 so as to be disposed at a portion of the predetermined width of the orbiting mirror plate 151, so that the center of gravity of the orbiting bearing 173 is lower than the compression chamber. Since it is prevented from being located at the bottom, the occurrence of tilting is reduced, and also, the occurrence of deformation in the inner circumference of the turning head plate portion 151 is also reduced.

The scroll compressor 10 described above is not limited to the configuration and method of the embodiments described above, but the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

It is apparent to those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit and essential characteristics of the present invention. Accordingly, the above detailed description should not be construed as limiting 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.

Claims (13)

casing;
a fixed scroll installed inside the casing and equipped with a fixed wrap;
an orbiting scroll having an orbiting wrap that rotates with respect to the fixed scroll and engages with the stationary wrap to form a compression chamber;
a rotating shaft disposed in one direction inside the casing and installed on inner circumferences of the fixed scroll and the orbiting scroll to transmit rotational force to enable rotation of the orbiting scroll; and
And a swing bearing inserted between the inner circumference of the orbiting scroll and the outer circumference of the rotation shaft,
The orbiting scroll is provided with a rotating shaft coupling part passing through an inner end of the orbiting wrap in an axial direction on one side of the orbiting mirror plate unit and receiving the orbiting bearing inserted into an inner circumference thereof;
At least a part of one end of the swing bearing overlaps the swing mirror plate portion in the axial direction,
One end of the swing bearing is axially spaced apart from one end of the swing mirror plate part,
Among the predetermined widths of the swing mirror plate portion, the width of the portion where the swing bearing is inserted is h, the height of the swing bearing is H, h / H has a value between 0.1 and 0.3,
The scroll compressor of claim 1 , wherein the predetermined width of the orbiting mirror plate is W, and h/W has a value between 0.2 and 0.4. delete delete According to claim 1,
Among the predetermined widths of the swinging mirror plate portion, the width of the portion where the swing bearing is inserted is h, the distance between the other end of the swing bearing and the end surface of the swing wrap is h1, and h>h1. Scroll compressor. According to claim 1,
A scroll compressor having a coupling end protruding in a radial direction to contact one end of the swing bearing and support the swing bearing at one end of the inner circumferential surface of the rotation shaft coupling portion. According to claim 1,
The orbiting scroll is a scroll compressor made of Al. casing;
a fixed scroll installed inside the casing and provided with a fixed wrap and a sub bearing hole;
an orbiting scroll having an orbiting wrap that rotates with respect to the fixed scroll and engages with the stationary wrap to form a compression chamber; and
A rotation shaft disposed in one direction inside the casing and installed on the inner circumference of the sub shaft hole and the orbiting scroll to transmit rotational force to enable rotation of the orbiting scroll,
The rotating shaft is inserted into the sub-shaft hole and has a fixed bearing portion supported in a radial direction,
Between the inner circumference of the orbiting scroll and the outer circumference of the rotating shaft, a swing bearing supporting the orbiting scroll so as to be able to rotate is inserted,
One end of the swing bearing is inserted into the inner circumference of the orbiting scroll so as to be disposed at a portion of a predetermined width of the orbiting mirror plate;
One end of the swing bearing is axially spaced apart from one end of the swing mirror plate part,
Among the predetermined widths of the swing mirror plate portion, the width of the portion where the swing bearing is inserted is h, the height of the swing bearing is H, h / H has a value between 0.1 and 0.3,
The scroll compressor of claim 1 , wherein the predetermined width of the orbiting mirror plate is W, and h/W has a value between 0.2 and 0.4. delete delete According to claim 7,
The width of the part where the swing bearing is inserted among the predetermined widths of the swing mirror plate part is h, the distance between the other end of the swing bearing and the end surface of the swing wrap is h1, and h > h1. Scroll compressor. The method of any one of claims 7 and 10,
The scroll compressor of claim 1 , wherein the orbiting scroll is provided with a rotational shaft coupling portion formed to pass through the orbiting wrap along a disposition direction of the rotational shaft and accommodating the rotational bearing so as to be inserted therein. According to claim 11,
The rotary shaft coupling part has a coupling end that contacts one end of the swing bearing and supports the swing bearing. According to claim 7,
The orbiting scroll is a scroll compressor made of Al.

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