KR102510338B1 - Scroll compressor - Google Patents

Abstract

According to the present invention, a scroll compressor comprises an Oldham ring including: a ring body having an annular shape and having at least one key accommodating groove; and at least one key having a first key portion provided at one end thereof to be inserted into the key accommodating groove, and a second key portion provided at the other end thereof to be inserted into the key accommodating groove. The first key portion can be rotatably inserted into the key accommodating groove. Therefore, the key of the Oldham ring rotates in the direction in which the same receives force from the key accommodating groove of a turning scroll (or frame), so that the key maintains surface contact with the key accommodating groove, to suppress the friction loss and wear of the key or the key groove, thereby improving compressor efficiency. In addition, the tolerance for the ring body and the key of the Oldham ring is increased to easily manufacture the Oldham ring, so that the manufacturing cost of the Oldham ring can be reduced. In addition, motor efficiency can be improved by reducing the weight of the Oldham ring by forming a portion of the Oldham ring of a light material.

Description

Scroll Compressor {SCROLL COMPRESSOR}

The present invention relates to an Oldham ring and a scroll compressor having the same.

A scroll compressor is a compressor that forms a compression chamber in which one or two scrolls facing each other continuously move while rotating. The scroll compressor may include a self-cleaning prevention member that prevents a scroll (eg, an orbiting scroll) receiving rotational force of a driving motor from rotating relative to another scroll (eg, a fixed scroll) or a fixed frame facing each other.

As an anti-rotation member, an Oldham ring or a pin & ring is mainly known. The Oldham ring has an advantage in terms of assembly compared to the pin and ring. Recently, a technology for reducing the weight while securing necessary rigidity by using different materials for a ring body and a key constituting an Oldham ring has been introduced.

On the other hand, in the Oldham ring, a sliding gap is formed between the side surfaces provided on both sides of the circumferential direction of the key, that is, the transverse side surface orthogonal to the radial direction and the transverse side surface of the key groove. As a result, the key slides in the radial direction inside the key groove provided in the scroll (or frame) to limit the rotation of the orbiting scroll coupled to the rotation shaft. However, when the compressor is aligned (before operation), the parallel state between the key and the keyway is maintained, but during the operation of the compressor, the parallelism between the key and the keyway is distorted due to the sliding interval, so that the parallelism cannot be maintained. As a result, line contact occurs between one transverse side of the key and the transverse side of the key groove facing it, and due to this line contact, the formation of an oil film between the key and the key groove is poor, resulting in abnormal wear. .

Patent Document 1 (US Patent Publication No. 2017/0234313 A1) discloses a technique in which the ring body and the key are formed of different materials, but the protrusions provided on the ring body are press-fitted or bonded to holes provided in the key. . In Patent Document 1, as the protrusions of the ring body and the holes of the key are formed into corresponding polygons so as to be engaged with each other, the key is firmly coupled to the ring body in an unfree state so that it cannot rotate with respect to the ring body. Accordingly, in Patent Document 1, strong linear contact occurs between the key and the keyway described above during operation of the compressor, which may increase friction loss and wear. In addition, in Patent Document 1, tolerances for processing and assembly of the ring body and the key must be kept to a minimum so that the protrusion of the ring body and the hole of the key are closely inserted. As a result, it is difficult to manufacture the Oldham ring including the ring body and the key, which may increase manufacturing cost.

Patent Document 2 (Japanese Patent Laid-Open Publication No. 2017-133466) discloses a technology in which a ring body and a key constituting an Oldham ring are integrally formed, and a separate wear-resistant member is interposed between the key of the Oldham ring and the keyway of a scroll (or frame). are starting However, in Patent Document 2, the material cost increases as a separate wear-resistant member must be added, and the wear-resistant member escapes during operation of the compressor due to the difference in thermal expansion rate between the wear-resistant member and the scroll (or fixed frame) Otherwise, vibration noise may be generated due to the loosening of the press-fitting band. In addition, in Patent Document 2, as the ring body of the Oldham ring and the key are integrally formed, friction loss and wear due to line contact between the key and the keyway as in Patent Document 1 may occur in the same way.

Patent Document 3 (Japanese Unexamined Patent Publication No. 2014-202076) discloses a technique of forming a radial protrusion on the outer surface of a key so that the radial protrusion is bent in a direction in which a force is applied so that it makes surface contact with the side surface of the key groove. In Patent Document 3, the parallel state of the radial protrusion must be actively or resiliently varied according to the rotation angle of the orbiting scroll. It is difficult to make it deformable. This not only increases the manufacturing cost, but also does not have a substantial friction loss reduction and wear prevention effect.

US Patent Publication 2017/0234313 A1 (published date: 2017.08.17.) Japanese Patent Laid-Open No. 2017-133466 (published date: 2017.08.03.) Japanese Patent Laid-open 2014-202076 (published date: 2014.10.27.)

An object of the present invention is to provide a scroll compressor capable of reducing friction loss and wear between an Oldham ring, which is an anti-rotation mechanism, and a member to which the Oldham ring is coupled.

Furthermore, an object of the present invention is to provide a scroll compressor capable of reducing friction loss and wear by lowering the surface pressure between an Oldham ring and a member with which the Oldham ring is in contact.

Furthermore, an object of the present invention is to provide a scroll compressor in which oil can be smoothly supplied between an Oldham ring or a member to which the Oldham ring is coupled.

Furthermore, the present invention provides a scroll compressor capable of increasing motor efficiency by reducing the weight of the Oldham ring while reducing friction loss and wear between the Oldham ring or members to which the Oldham ring is coupled.

Another object of the present invention is to provide a scroll compressor capable of easily fabricating an Oldham ring to reduce manufacturing cost and increase reliability.

Furthermore, an object of the present invention is to provide a scroll compressor capable of easily manufacturing an Oldham ring by increasing tolerance for an assembly structure between a ring body and a key of the Oldham ring.

Furthermore, an object of the present invention is to provide a scroll compressor capable of effectively suppressing rotation of an orbiting scroll while easily assembling a ring body and a key of an Oldham ring.

Furthermore, an object of the present invention is to provide a scroll compressor capable of suppressing separation of the key from the ring body while easily assembling the key and the ring body of the Oldham ring.

In order to achieve the object of the present invention, a plurality of scrolls including orbiting scrolls that are engaged with each other and at least one of the scrolls is coupled to a rotation shaft to perform orbital motion may be included. A scroll compressor may include an Oldham ring that is slidably coupled to a keyway provided in the orbiting scroll and induces an orbital motion of the orbiting scroll. The Oldham ring is formed in an annular shape and includes a ring body having at least one key receiving groove, one end having a first key part inserted into the key receiving groove, and the other end having the key groove. It may include at least one or more keys provided with a second key unit inserted into. The first key unit may be rotatably inserted into the key receiving groove. Through this, while the key of the Oldham ring rotates in the direction of receiving the force in the keyway of the orbiting scroll (or frame), the key maintains surface contact with the keyway, suppressing frictional loss and wear of the key or keyway to increase compressor efficiency. there is. In addition, the manufacturing cost of the Oldham ring can be lowered by easily manufacturing the Oldham ring by increasing the tolerance for the ring body and the key of the Oldham ring. In addition, a part of the Oldham ring is formed of a light material to reduce the weight of the Oldham ring, thereby improving motor efficiency.

For example, a rotation interval spaced apart in a radial direction may be provided between an inner circumferential surface of the key receiving groove and an outer circumferential surface of the first key unit. Through this, the key of the Oldham ring is coupled to the ring body in a free rotation state, and surface contact with the keyway can be maintained.

Specifically, a sliding interval spaced apart in a lateral direction may be provided between the second key portion and the key groove. The rotation interval may be smaller than or equal to the sliding interval. Through this, while the key of the Oldham ring freely rotates with respect to the ring body, the key suppresses rotation of the orbiting scroll, thereby increasing compressor efficiency.

As another example, at least one of the inner circumferential surface of the key receiving groove and the outer circumferential surface of the first key portion may be formed in a circular cross-sectional shape. Through this, the key of the Oldham ring can be coupled to the ring body in a free rotation state.

As another example, both transverse side surfaces of the second key part may be formed in parallel. Through this, it is possible to secure surface contact between the second key portion and the key groove in contact therewith.

For example, the second key portion may be formed in a rectangular cross-sectional shape in which a radial length is longer than a lateral length. Through this, it is possible to secure a wide contact area between the second key portion and the key groove in contact therewith.

For example, the second key portion may have a radial length equal to or smaller than a lateral length. Through this, motor efficiency can be increased by reducing the weight of the second key unit and reducing the overall weight of the Oldham ring while securing a wide contact area between the second key unit and the key groove contacting the second key unit.

As another example, the first key part and the second key part may be formed as a single body. Through this, the key of the Oldham ring can be easily manufactured.

As another example, the first key unit may be inserted into and coupled to the second key unit. Through this, it is possible to reduce the weight of the Oldham ring or reduce the manufacturing cost by increasing the degree of freedom in selecting the material of the first key part and the second key part.

Specifically, the first key portion may be formed of a harder material than the second key portion. Through this, the weight of the Oldham ring can be further reduced to increase motor efficiency.

As another example, the outer circumferential surface of the first key portion may be formed in a smooth tube shape. Through this, it is possible to easily manufacture the key of the Oldham ring that rotates freely in the ring body.

As another example, an oil supply passage may be formed in a straight line or an oblique line along an axial direction on at least one of an outer circumferential surface or inner surface of the first key unit and an inner circumferential surface of the key receiving groove. Through this, oil is smoothly supplied between the key of the Oldham ring and the ring body so that the key rotates smoothly with respect to the ring body, so that the key can continuously maintain a surface contact state with the keyway.

Specifically, an oil supply passage may be further provided in the second key part. An oil supply passage provided in the second key unit may be formed on a lateral side surface of the second key unit that is in sliding contact with the key groove. Through this, oil can be smoothly supplied between the key and the keyway of the Oldham ring, and thus friction loss and wear can be further reduced.

For example, oil supply passages may be formed in the second key part and the first key part, respectively. A storage groove recessed to a predetermined depth may be formed on an end surface of the second key unit. The oil supply passage may communicate with the oil storage groove. Through this, not only is an appropriate amount of oil supplied between the key and the keyway when the compressor is running, but also a certain amount of O-ring is stored in the oil storage groove when the compressor is stopped, and oil can be quickly supplied between the key and the keyway when the compressor is restarted.

As another example, among both ends of the first key unit in the axial direction, a key binding unit extending in a radial direction may be further provided at an opposite end of the second key unit. The key restraining part may be formed larger than the inner diameter of the key receiving groove. Through this, separation of the key from the ring body is prevented, thereby facilitating assembly of the key and the ring body, and suppression of jumping of the key from the ring body to suppress abrasion or abnormal noise.

Here, the ring body may be formed of the same material as the orbiting scroll. The key may be formed of a different material from the ring body. Through this, a part of the Oldham ring is formed of a light material to reduce the weight of the Oldham ring, thereby improving motor efficiency.

In order to achieve the object of the present invention, a plurality of scrolls including orbiting scrolls that are engaged with each other and at least one of the scrolls is coupled to a rotation shaft to perform orbital motion may be included. An Oldham ring that is slidably coupled to a keyway provided in the orbiting scroll and induces a orbital motion of the orbiting scroll may be included. The Oldham ring may include a ring body formed in an annular shape. It may include a key that is rotatably coupled to the ring body and is slidably coupled to the key groove. Through this, while the key of the Oldham ring rotates in the direction of receiving the force in the keyway of the orbiting scroll (or frame), the key maintains surface contact with the keyway, suppressing frictional loss and wear of the key or keyway to increase compressor efficiency. there is. In addition, the manufacturing cost of the Oldham ring can be lowered by easily manufacturing the Oldham ring by increasing the tolerance for the ring body and the key of the Oldham ring.

For example, at least one key receiving groove may be provided in the ring body. The key may include a first key unit rotatably inserted into the key receiving groove. A second key portion extending from the first key portion and slidingly inserted into the key groove may be included. Through this, the reliability of the key can be increased by enlarging the diameter of the first key part under the same conditions as for the ring body.

As another example, the key may include a first key portion extending axially from the ring body. It may include a second key portion that is slidably coupled to the key groove and is provided with a key receiving groove so that the first key portion is rotatably inserted therein. Through this, since the first key portion is formed of the same hard material as the ring body, the weight of the Oldham ring including the key can be reduced to increase motor efficiency.

Specifically, a rotation interval may be formed between the first key portion and the key receiving groove. A sliding gap may be formed between the second key portion and the key groove. The rotation interval may be smaller than or equal to the sliding interval. Through this, while the key of the Oldham ring freely rotates with respect to the ring body, the key suppresses rotation of the orbiting scroll, thereby increasing compressor efficiency.

In the scroll compressor according to the present invention, the Oldham ring is formed in an annular shape and has a ring body having at least one key receiving groove, one end having a first key part inserted into the key receiving groove, and the other end having a ring body. At least one key having a second key unit inserted into the key groove may be included, and the first key unit may be rotatably inserted into the key receiving groove. Through this, while the key of the Oldham ring rotates in the direction of receiving the force in the keyway of the orbiting scroll (or frame), the key maintains surface contact with the keyway, suppressing frictional loss and wear of the key or keyway to increase compressor efficiency. there is. In addition, the manufacturing cost of the Oldham ring can be lowered by easily manufacturing the Oldham ring by increasing the tolerance for the ring body and the key of the Oldham ring. In addition, a part of the Oldham ring is formed of a light material to reduce the weight of the Oldham ring, thereby improving motor efficiency.

In the scroll compressor according to the present invention, a radially spaced rotation distance is provided between the inner circumferential surface of the key receiving groove and the outer circumferential surface of the first key part, and a sliding distance spaced apart in the transverse direction between the second key part and the key groove It is provided, and the rotation interval may be smaller than or equal to the sliding interval. Through this, the key of the Oldham ring is coupled to the ring body in a free rotation state, so that the key restrains rotation of the orbiting scroll while maintaining surface contact with the key groove, thereby increasing compressor efficiency.

In the scroll compressor according to the present invention, at least one of the inner circumferential surface of the key receiving groove and the outer circumferential surface of the first key part is formed in a circular cross-sectional shape, and the second key part may have both transverse side surfaces parallel to each other. Through this, the key of the Oldham ring is coupled to the ring body in a free rotation state, so that surface contact between the second key portion and the key groove in contact therewith can be secured.

In the scroll compressor according to the present invention, the second key portion may be formed in a rectangular cross-sectional shape in which a radial length is longer than a lateral length. Through this, it is possible to secure a wide contact area between the second key portion and the key groove in contact therewith.

In the scroll compressor according to the present invention, the second key portion may have a radial length equal to or smaller than a transverse length. Through this, motor efficiency can be increased by reducing the weight of the second key unit and reducing the overall weight of the Oldham ring while securing a wide contact area between the second key unit and the key groove contacting the second key unit.

In the scroll compressor according to the present invention, a first oil supply passage is formed on at least one of the outer circumferential surface or inner surface of the first key part and the inner circumferential surface of the key receiving groove, and a second oil supply passage is formed in the second key part. there is. Through this, oil is smoothly supplied between the key of the Oldham ring and the ring body so that the key rotates smoothly with respect to the ring body, so that the key can continuously maintain a surface contact state with the keyway. In addition, friction loss and wear can be further reduced by smoothly supplying oil between the key and the keyway of the Oldham ring.

In the scroll compressor according to the present invention, an oil supply passage is formed in the second key part and the first key part, and an oil storage groove recessed by a predetermined depth is formed on an end surface of the second key part, and the oil supply passage is formed in the oil supply passage. It can communicate with the oil reservoir. Through this, not only is an appropriate amount of oil supplied between the key and the keyway when the compressor is running, but also a certain amount of O-ring is stored in the oil storage groove when the compressor is stopped, and oil can be quickly supplied between the key and the keyway when the compressor is restarted.

In the scroll compressor according to the present invention, a key restraining part extending in a radial direction is provided at an opposite end of the second key part among both ends in an axial direction of the first key part, and the key restraining part is formed to have a larger inner diameter than the key receiving groove. It can be. Through this, separation of the key from the ring body is prevented, thereby facilitating assembly of the key and the ring body, and suppression of jumping of the key from the ring body to suppress abrasion or abnormal noise.

In the scroll compressor according to the present invention, the key includes a first key portion extending axially from the ring body, is slidably coupled to the key groove, and has a key receiving groove so that the first key portion is rotatably inserted. A provided second key unit may be included. Through this, since the first key portion is formed of the same hard material as the ring body, the weight of the Oldham ring including the key can be reduced to increase motor efficiency.

1 is a cross-sectional view showing a scroll compressor according to this embodiment;
Figure 2 is an exploded perspective view showing a part of the compression unit in Figure 1;
3 is an enlarged perspective view of a part of the Oldham ring in FIG. 2;
4 is a sectional view "IV-IV" of FIG. 3;
5 is a cross-sectional view "V-V" of FIG. 3;
6A and 6B are schematic diagrams shown to explain the correspondence between the second keyway and the second key in FIG. 3;
FIG. 7 is a cross-sectional view illustrating a fuel supply state around the Oldham Ring in FIG. 1;
8 and 9 are perspective and cross-sectional views showing another embodiment of the Oldham ring;
10 and 11 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring;
12 and 13 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring;
14 and 15 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring;
16 and 17 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring;
18 is a perspective view showing another embodiment of a second key of the Oldham ring;
19 is a cross-sectional view showing another embodiment of the second key of the Oldham ring;
20 and 21 are exploded perspective views and assembled cross-sectional views showing other embodiments of the Oldham ring.

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

The scroll compressor may be divided into a closed type or an open type depending on whether the drive motor and the compression unit are installed together in the inner space of the casing. In the closed type, the drive motor and the compression unit are installed together in the inner space of the casing, and in the open type, the drive motor (or drive source) is installed outside the casing. This embodiment will be described taking a hermetic scroll compressor as a representative example. However, the same can be applied to an open scroll compressor.

Also, scroll compressors may be classified into fixed scroll compressors and movable scroll compressors. The fixed type is usually applied for building air conditioning, and the mobile type is applied for vehicle air conditioning. This embodiment will be described using a fixed scroll compressor as a representative example. However, the same can be applied to a movable scroll compressor.

In addition, the scroll compressor may be classified into a low pressure type or a high pressure type according to the pressure of the refrigerant filled in the inner space of the casing. In the low pressure type, the inner space of the casing is filled with the refrigerant of the suction pressure, and in the high pressure type, the inner space of the casing is filled with the refrigerant of the discharge pressure. This embodiment will be described using a high-pressure scroll compressor as a representative example. However, the same can be applied to low-pressure scroll compressors.

In addition, the scroll compressor may be divided into an upper compression type and a lower compression type according to the installation position of the compression unit. In the upper compression type, the compression unit is installed above the drive motor, and in the bottom compression type, the compression unit is installed below the drive motor. This embodiment will be described taking an upper compression type scroll compressor as a representative example. However, the same can be applied to a bottom compression type scroll compressor.

In addition, scroll compressors may be classified into single-rotation scroll compressors and mutually-rotating scroll compressors according to whether or not the scroll rotates. The single-rotation scroll compressor is configured so that one scroll is fixed or limited in rotation while the other scroll is rotated, and the mutual rotation scroll compressor is configured to allow both scrolls to rotate. This embodiment will be described taking a one-rotation scroll compressor as a representative example. However, the same can be applied to mutually rotating scroll compressors.

In addition, the scroll compressor according to the present embodiment can be equally applied to all scroll compressors to which the Oldham ring is applied.

1 is a cross-sectional view showing a scroll compressor according to an embodiment.

Referring to FIG. 1 , in the scroll compressor according to the present embodiment, a drive motor 120 may be installed in the lower half of the casing 110 and a main frame 130 may be installed in the upper side of the drive motor 120 . A compression unit is installed on the upper side of the main frame 130 . The compression unit includes the fixed scroll 140 and the orbiting scroll 150, but in some cases, the main frame 130 may also be included in the compression unit.

The casing 110 according to the present embodiment may include a cylindrical shell 111, an upper cap 112, and a lower cap 113. Accordingly, the inner space 110a of the casing 110 includes the upper space 110b provided inside the upper cap 112 and the intermediate space provided inside the cylindrical shell 111 based on the flow order of the refrigerant ( 110c), and a lower space 110d provided inside the lower cap 113. Hereinafter, the upper space 110b may be defined as a discharge space, the middle space 110c as an oil separation space, and the lower space 110d as a storage space.

The cylindrical shell 111 has a cylindrical shape with both upper and lower ends open, and the driving motor 120 and the main frame 130 are press-fitted and fixed to the lower half and the upper half to the inner circumferential surface of the cylindrical shell 111, respectively.

A refrigerant discharge pipe 116 penetrates and is coupled between the intermediate space 110c of the cylindrical shell 111, specifically between the driving motor 120 and the main frame 130. The refrigerant discharge pipe 116 may be directly inserted into and welded to the cylindrical shell 111, but usually a collar pipe (not shown) made of the same material as the cylindrical shell 111 is attached to the cylindrical shell 111. It is inserted and welded, and the refrigerant discharge pipe 116 made of copper can be inserted and welded to the intermediate connecting pipe.

The upper cap 112 is coupled to cover the open top of the cylindrical shell 111 . A refrigerant suction pipe 115 penetrates and is coupled to the upper cap 112, and the refrigerant suction pipe 115 passes through the upper space 110b of the casing 110 and is directly connected to a suction chamber (unmarked) of the compression unit to be described later. . Accordingly, the refrigerant may be supplied to the suction chamber through the refrigerant suction pipe 115 .

The lower cap 113 is coupled to cover the opened lower end of the cylindrical shell 111 . The lower space 110d of the lower cap 113 forms an oil storage space, and a predetermined amount of oil may be stored in the storage space. The lower space 110d constituting the storage oil space may communicate with the upper space 110b and the middle space 110c of the casing 110 through an oil return passage (not shown). Accordingly, the oil separated from the refrigerant in the upper space 110b and the middle space 110c and the oil supplied to the compression unit and then recovered are returned to the lower space 110d constituting the storage space through the oil return passage and stored. can

1, the drive motor 120 according to the present embodiment is installed in the lower half of the intermediate space 110c constituting the high-pressure part in the inner space 110a of the casing 110, and the stator 121 and the rotor ( 122). The stator 121 is fixed to the inner wall surface of the cylindrical shell 111 by hot press-fitting, 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 a cylindrical shape and fixed to the inner circumferential surface of the cylindrical shell 111 by hot press fitting. The stator coil 121a is wound around the stator core 1211 and is electrically connected to an external power source through terminals (unsigned) penetrated into the casing 110.

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

The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the stator core 1211 at intervals equal to a preset air gap. The permanent magnets 1222 are embedded in the rotor core 1221 at predetermined intervals along the circumferential direction.

The rotating shaft 125 is press-fitted and coupled to the rotor 122 . The upper end of the rotary shaft 125 is provided with an eccentric part and is rotatably supported by the main frame 130 to be described later in the radial direction, and the lower end of the rotary shaft 125 is rotatably radially and axially supported by the subframe 118. supported

In addition, an oil supply hole 1255 may be formed inside the rotating shaft 125 passing between both ends of the rotating shaft 125 . The oil supply hole 1255 may be formed through the bottom surface of the eccentric part 1251 at the lower end of the rotating shaft 125 . Accordingly, the oil stored in the lower space 110d constituting the storage space may be supplied to the inside of the eccentric part 1251 through the oil supply hole 1255.

In addition, an oil pickup 126 may be installed at the lower end of the rotary shaft 125, more precisely at the lower end of the oil supply hole 1255. The oil pickup 126 may be installed to be submerged in oil stored in the oil storage space 110d. Accordingly, the oil stored in the storage space 110d may be pumped by the oil pickup 126 and sucked through the oil supply hole 1255.

Referring to FIG. 1 , the main frame 130 according to the present embodiment is installed above the driving motor 120 and fixed to the inner wall surface of the cylindrical shell 111 by hot press fitting or by welding. Accordingly, the main frame 130 is usually formed of cast iron.

The main frame 130 includes a main flange portion 131 and a shaft support protrusion 132 .

The main flange portion 131 is formed in an annular shape and accommodated in the intermediate space 110c of the cylindrical shell 111 . For example, the outer circumferential surface of the main flange portion 131 may be formed in a circular shape and closely adhered to the inner circumferential surface of the cylindrical shell 111 . In this case, at least one oil return hole (not shown) penetrating in the axial direction may be formed between the outer and inner circumferential surfaces of the main flange portion 131 .

In addition, at least one frame fixing protrusion (not marked) may be formed extending in the radial direction on the outer circumferential surface of the main flange portion 131 . The outer circumferential surface of the frame fixing protrusion may be fixed in close contact with the inner circumferential surface of the cylindrical shell 111 . In this case, the frame fixing protrusions may be spaced apart in the circumferential direction to form second discharge passage grooves 1421 penetrating between both side surfaces of the main flange portion 131 in the axial direction. The second discharge passage groove 1421 may be formed to communicate with each other on the same axis as the first discharge passage groove 1421 to be described later. Accordingly, the upper space 110b and the middle space 110c communicate with each other so that the refrigerant discharged from the compression unit to the upper space 110b moves to the middle space 110c and is discharged toward the condenser through the refrigerant discharge pipe 116. It can be.

In addition, an Oldham ring accommodating portion (not shown) may be formed on the upper surface of the main flange portion 131, and a first key groove (not shown) may be formed in the Oldham ring accommodating portion. Two first key grooves may be formed with a phase difference of about 180° along the circumferential direction.

A first key 162 of an Oldham ring 160, which will be described later, can be inserted radially into the first key groove. In this case, a liner constituting a wear-resistant member is inserted into the first keyway, or the first key 162 of the Oldham ring 160 inserted into the first keyway is connected to the ring body 161 of the Oldham ring 160. It may be formed of a different material (different material).

For example, when the main frame 130 is made of the same material as the first key 162 of the Oldham ring 160, wear between the main frame 130 and the Oldham ring 160 is suppressed. A liner made of a material different from that of the main frame 130 or the Oldham ring 160 may be provided. Alternatively, the first key 162 may be assembled to the ring body 161 constituting the Oldham ring 160 after being assembled, and the first key 162 may be formed of a material different from that of the main frame 130 . However, as in the present embodiment, the main frame 130 and the ring body 161 of the Oldham ring 160 are formed of different materials (eg, the main frame is cast iron and the first key of the Oldham ring is aluminum). In this case, there is no need to install a separate liner in the first keyway.

The shaft support protrusion 132 extends toward the driving motor 120 from the center of the main flange portion 131, and a shaft support hole 1321 is formed inside the shaft support protrusion 132. The shaft support hole 1321 may be formed through both side surfaces of the main flange portion 131 in the axial direction. Accordingly, the main flange portion 131 may be formed in an annular shape.

Referring to FIG. 1 , a fixed scroll 140 according to the present embodiment may include a fixed head plate 141 , a fixed side wall portion 142 and a fixed wrap 143 .

The fixed end plate 141 may be formed in a disk shape. The outer circumferential surface of the fixed end plate 141 may be formed to be in close contact with the inner circumferential surface of the upper cap 112 constituting the upper space 110b or may be formed to be spaced apart from the inner circumferential surface of the upper cap 112 .

In addition, a suction port 1411 is formed at the edge of the fixed head plate portion 141 through the axial direction and communicates with the suction chamber (unsigned), and the suction port 1411 penetrates the upper cap 112 of the casing 110. The refrigerant suction pipe 115 to be inserted can be coupled. Accordingly, the refrigerant suction pipe 115 may pass through the upper space 110b of the casing 110 and directly communicate with the suction port 1411 of the fixed scroll 140.

In addition, a discharge port 1412 and a bypass hole (not shown) are formed in the center of the fixed head plate portion 141, and a discharge valve 145 for opening and closing the discharge port 1412 and a bypass hole are formed on the upper surface of the fixed head plate portion 141. A bypass valve (not shown) may be installed to open and close the pass hole. Accordingly, the refrigerant compressed in the compression chamber (V) is discharged from the upper side of the fixed scroll (140) to the upper space (110b) formed in the upper cap (112).

The fixed side wall portion 142 may extend annularly toward the main frame 130 from the edge of the fixed end plate portion 141 . Accordingly, the lower surface of the fixed side wall portion 142 may be in close contact with the upper surface of the main frame 130, that is, the upper surface of the main flange portion 131 and fastened with bolts.

At least one or more first discharge passage grooves 1421 may be formed on an outer circumferential surface of the fixed side wall portion 142 . The first discharge passage groove 1421 may be recessed in the outer circumferential surface of the fixed scroll 140 to communicate between both side surfaces of the fixed scroll 140 in the axial direction. For example, the first discharge passage groove 1421 may be formed to communicate from the upper surface of the fixed end plate portion 141 to the lower surface of the fixed side wall portion 142 . Accordingly, the upper end of the first discharge passage groove 1421 is in communication with the upper space 110b, and the lower end of the first discharge passage groove 1421 is the second discharge passage groove 1421 provided in the main frame 130 ( 1311) may be communicated to the top.

The fixed wrap 143 may extend toward the orbiting scroll 150 from the lower surface of the fixed end plate 141 . The fixing wrap 143 may be formed in various shapes such as an involute. The stationary wrap 143 may be engaged with the orbiting wrap 153 to be described later to form a pair of compression chambers V.

Referring to FIG. 1 , the orbiting scroll 150 according to the present embodiment may include an orbiting head plate unit 151, a rotation shaft coupling unit 152, and an orbiting wrap 153.

The orbiting mirror plate unit 151 is formed in a disk shape, is supported in the axial direction by the main frame 130, and is provided to perform a pivoting movement between the main frame 130 and the fixed scroll 140.

A second key groove 1511 into which a second key 163 of the Oldham ring 160 to be described later is slidably inserted may be provided on one side of the orbiting mirror plate 151, that is, on the opposite side of the orbiting wrap 153. . The second key groove 1511 may be provided with a phase difference of about 180° along the circumferential direction.

The second key groove 1511 extends a predetermined length from the outer circumferential surface of the turning head plate 151 toward the rotary shaft coupling part 152 so that the second key 163 of the Oldham ring 160, which will be described later, is slid in the radial direction. It can be formed recessed. The second keyway 1511 will be described again together with the Oldham ring 160 later.

The rotating shaft coupling portion 152 may extend from the geometric center of the orbiting scroll 150 toward the eccentric portion 1251 of the rotating shaft 125 . The rotating shaft coupling portion 152 may be rotatably inserted into the eccentric portion 1251 of the rotating shaft 125 . Accordingly, the orbiting scroll 150 is rotated by the eccentric part 1251 of the rotary shaft 125 and the rotary shaft coupling part 152.

The orbiting wrap 153 may extend toward the fixed scroll 140 from the upper surface of the orbiting mirror plate 151 . The orbiting wrap 153 may be formed in various shapes such as an involute to correspond with the stationary wrap 143 .

The Oldham ring 160 may be provided between the main frame 130 and the orbiting scroll 150 . However, in some cases, the Oldham ring 160 may be provided on the fixed scroll 140 and the orbiting scroll 150. This embodiment will be described focusing on an example in which the Oldham ring 160 is provided between the main frame 130 and the orbiting scroll 150.

For example, the Oldham ring 160 may be slidably coupled to the main frame 130 and the orbiting scroll 150, respectively. Accordingly, the Oldham ring 160 restricts the rotation of the orbiting scroll 150 so that the orbiting scroll 150 orbits relative to the main frame 130 . The Oldham ring 160 will be described later.

Effects of the scroll compressor according to the present embodiment as described above are as follows.

That is, when power is applied to the driving motor 120 and rotational force is generated, the orbiting scroll 150 eccentrically coupled to the rotational shaft 125 rotates with respect to the fixed scroll 140 by the Oldham ring 160. . At this time, between the fixed scroll 140 and the orbiting scroll 150, two pairs of compression chambers V continuously move are formed.

Then, the volume of the compression chamber V is gradually reduced while moving from the suction port (or suction chamber) 1411 toward the discharge port (or discharge chamber) 1412 while the orbiting scroll 150 performs the orbiting motion.

Then, the refrigerant flows into the compression chamber V through the suction port 1411 of the fixed scroll 140 through the refrigerant suction pipe 115, and the refrigerant is compressed while moving toward the final compression chamber by the orbiting scroll 150. do. This refrigerant is discharged from the final compression chamber to the upper space 110b of the casing 110 through the discharge port 1412 of the fixed scroll 140, and is discharged through the first discharge passage groove 1421 and the second discharge passage groove 1311. The refrigerant moves to the intermediate space 110c or/and the lower space 110d of the casing 110 through the refrigerant guide passage.

Then, while the refrigerant circulates in the inner space 110a of the casing 110, the oil is separated from the refrigerant, and the oil separated from the refrigerant is moved to the storage space constituting the lower space 110d of the casing 110 and stored. A series of processes in which oil is supplied to the compression unit through the oil pickup 126 and the oil supply hole 1255 of the rotary shaft 125, while the refrigerant from which oil is separated is discharged to the outside of the casing 110 through the refrigerant discharge pipe 116. will repeat

Meanwhile, as described above, the orbiting scroll is slidably coupled to the Oldham ring to perform orbital motion with respect to the fixed scroll and/or the main frame. Accordingly, it is advantageous to increase motor efficiency by reducing centrifugal force caused by the Oldham ring by making the orbiting scroll and the Oldham ring as light as possible.

Accordingly, conventionally, a technique for manufacturing the orbiting scroll and the Oldham ring using an aluminum alloy material (hereinafter referred to as aluminum) is known. In this case, the ring body and the second key of the Oldham ring are made of different materials, but the ring body is made of aluminum, the same material as the orbiting scroll, while the second key is made of iron, such as cast iron, which is a different material from the orbiting scroll. material can be formed.

However, as in Patent Document 1 described above, when the second key is press-fitted and integrally coupled to the ring body, or when the second key is formed in a single body as in Patent Document 2 and Patent Document 3, the key for linear motion Abnormal wear between the key and the keyway may occur as the keyway for rotational motion is in line contact with the keyway. In addition, in the case of post-assembly of the ring body and the second key, since the assembly structure between the ring body and the second key must be precisely processed and assembled, tolerance for processing and assembly is small, so manufacturing costs may increase accordingly.

Therefore, in this embodiment, the ring body and the key of the Oldham ring are formed of different materials and then assembled, or a wear-resistant coating layer is formed on the key to be assembled after assembly, but the key can be formed to freely rotate with respect to the ring body. . Through this, surface contact between the key and the keyway suppresses abnormal wear between the key and the keyway, and at the same time, it is possible to reduce manufacturing costs by lowering the tolerance for processing and assembling the Oldham ring including the ring body and the key. Hereinafter, an example in which the ring body and the key of the Oldham ring are made of different materials will be mainly described.

FIG. 2 is an exploded perspective view showing a portion of the compression unit in FIG. 1, FIG. 3 is an enlarged perspective view of a portion of the Oldham ring in FIG. 2, FIG. 4 is a cross-sectional view “IV-IV” of FIG. It is a sectional view "V-V" of FIG.

2 to 5 , the Oldham ring 160 according to the present embodiment may include a ring body 161, a first key 162 and a second key 163.

The first key 162 and the second key 163 may be formed of a heterogeneous material different from that of the ring body 161, and either one of the first key 162 and the second key 163 is a ring body. The same material as (161), the other key may be formed of a different material from the ring body (161). In this embodiment, the first key 162 is made of the same material as the ring body 161 and the second key 163 is made of a different material different from that of the ring body 161.

The ring body 161 may be formed of the same material as the orbiting scroll 150, that is, aluminum. The specific gravity of cast iron used for the main frame 130 or the fixed scroll 140 is about 785, and the specific gravity of aluminum alloy is about 28. Accordingly, when the ring body 161 of the Oldham ring 160 is made of aluminum, the weight of the Oldham ring 160 is reduced, suppressing the increase in vibration and noise due to the reciprocating motion of the Oldham ring 160 during high-speed operation. At the same time, the manufacturing cost of the Oldham ring 160 can be reduced.

Referring to Figure 2, the ring body 161 according to this embodiment may be formed in an annular shape. The ring body 161 may be formed in a perfect circular shape, and in some cases may be formed in an elliptical shape. This embodiment will be described focusing on an example in which the ring body 161 is formed in a perfect circle shape.

The ring body 161 is formed in a perfect circular shape, and extension portions 1611 may be formed at appropriate locations along the circumferential direction. The expansion part 1611 is a part where the Oldham ring 160 is coupled to the main frame 130 and the orbiting scroll 150, and may be formed at intervals of about 90°.

The extension 1611 may extend radially. For example, the expansion part 1611 may extend radially from the outer circumferential surface of the ring body 161, and may extend radially from the inner circumferential surface of the ring body 161 in some cases. Of course, the extension part 1611 may also extend radially from the outer and inner circumferential surfaces of the ring body 161, respectively. In this embodiment, an example in which the expansion part 1611 extends in the radial direction from the outer circumferential surface of the ring body 161 will be mainly described.

The expansion part 1611 may extend long in the radial direction to secure the radial length of the first key 162 or/and the second key 163 . Accordingly, the first key 162 and the second key 163 secure a radial length sufficient to suppress the rotation of the orbiting scroll 150, while minimizing the radial width of the ring body 161 to come up with An increase in the weight of the dam ring 160 can be suppressed.

The extension 1611 may also extend in the axial direction. For example, the expansion part 1611 may extend in the axial direction by a predetermined height from one or both sides of the ring body 161 in the axial direction. Accordingly, in the ring body 161, the axial height (thickness) of the extension part 1611 is greater than the axial height (thickness) of parts other than the extension part 1611, so that the extension part 1611 is formed. The axial side surface of the main frame 130 or the orbiting scroll 150 may be supported in the axial direction in contact. Through this, the weight of the Oldham ring 160 can be reduced while the Oldham ring 160 is provided to slide between the main frame 130 and the orbiting scroll 150 .

In addition, the first key 162 and the second key 163 may be integrally extended or post-assembled on the axial side of the expansion part 1611 . For example, the expansion unit 1611 includes two first expansion units 1611a and two second expansion units 1611b, and each of the two first expansion units 1611a and the second expansion unit 1611b may be alternately formed along the circumferential direction.

The first extension 1611a is formed flat on both axial side surfaces, and the first key 162 passes through the first keyway of the main frame 130 on one side (lower surface) of the first extension 1611a. It may be integrally formed by extending in the axial direction toward each other. Accordingly, the first extension part 1611a constituting a part of the ring body 161 may be formed of the same material as the first key 162.

The second expansion part 1611b has both axial side surfaces flat, and a key receiving groove 1612 penetrating from one side (upper surface) to the other side (lower surface) of the second expansion part 1611b is formed. can A second key 163 provided in the orbiting scroll 150 may be rotatably inserted into the key receiving groove 1612 .

Referring to FIG. 2 , the key receiving groove 1612 according to the present embodiment may be formed in a circular cross-sectional shape. However, the key receiving groove 1612 does not necessarily have to be formed in a circular shape. If the first key portion 1631 of the second key 163 to be described later can be rotated in the key receiving groove 1612, the shape of the key receiving groove 1612 can be applied regardless of whether it is an elliptical shape or an angular shape. However, the key-receiving groove 1612 in this embodiment will be described based on an example having a circular cross-sectional shape.

The key receiving groove 1612 may be formed in the shape of a hole penetrating in the axial direction. However, the key-receiving groove 1612 may be formed in a recessed groove shape by a predetermined depth in the axial direction on the surface facing the orbiting scroll 150 . However, in this embodiment, it is formed in a hole shape, but for convenience, it is defined as a key receiving groove 1612 and described.

The inner diameter of the key receiving groove 1612 may be larger than the outer diameter of the first key portion 1631 of the second key 163 to be described later. Accordingly, a radially spaced rotation interval G1 may be formed between the inner circumferential surface of the key receiving groove 1612 and the outer circumferential surface of the first key portion 1631 of the second key 163 . The rotation interval G1 may be smaller than or equal to the sliding interval G2 to be described later.

Referring to FIG. 2, the first key 162 according to the present embodiment is downward toward the first key groove (unsigned) from one side of the first expansion part 1611a constituting the ring body 161 as described above. may be extended. Accordingly, the first key 162 may be formed of aluminum, which is the same material as the ring body 161 . This may be applied when the main frame 130 into which the first key 162 is slidably inserted is made of a material different from that of the Oldham ring 160, for example, cast iron. If the main frame 130 is made of the same material as the Oldham ring 160, that is, aluminum, the first key 162 is also post-assembled to the ring body 161 like the second key 163 described later. It can be. In this case, the ring body 161 is provided with other key receiving grooves (not shown) on both sides along the circumferential direction of the key receiving groove 1612 to which the second key 163 is coupled, respectively, so that the first key 162 may be rotatably coupled.

2 to 5, the second key 163 according to the present embodiment is the first key portion 1631 inserted into the key receiving groove 1612 of the ring body 161 and the turning scroll 150. A second key portion 1632 inserted into the second key groove 1511 may be included. As described above, the second key 163 may be formed of a different material from the orbiting scroll 150, that is, cast iron.

The first key portion 1631 may extend in an axial direction from the second key portion 1632 . For example, the first key portion 1631 is formed in a cylindrical shape extending toward the key receiving groove 1612 of the ring body 161 from one side in the axial direction of the second key portion 1632 facing the ring body 161. It can be. An outer circumferential surface of the first key portion 1631 may be formed in a substantially smooth smooth tube shape.

Referring to FIG. 5 , the outer diameter of the first key portion 1631 may be smaller than the inner diameter of the key receiving groove 1612 . For example, a rotation gap G1 may be formed between the outer circumferential surface of the first key unit 1631 and the inner circumferential surface of the key receiving groove 1612 . Accordingly, the first key unit 1631 is rotatably inserted into the key receiving groove 1612 in a free state, and the second key 163 is moved by an external force (the rotational force of the rotating shaft 125 applied to the orbiting scroll 150). It can be rotated within a certain range with respect to the ring body 161. Through this, the transverse side surface 1632a of the second key portion 1632 is in surface contact with the transverse side surface 1511a of the second keyway 1511 almost constantly, thereby minimizing the surface pressure between the key and the keyway. there is. Through this, friction loss and wear between the key and the keyway can be reduced.

The rotation interval G1 may be smaller than or equal to the sliding interval G2 to be described later. For example, the rotation distance G1 between the outer circumferential surface of the first key portion 1631 and the inner circumferential surface of the key receiving groove 1612 is the horizontal distance between the lateral side surface 1632a of the second key portion 1632 and the second key groove 1511. It may be formed smaller than or equal to the sliding distance G2 between the direction side surfaces 1511a. Accordingly, even if the direction of motion of the orbiting scroll 150 for rotational motion and the direction of motion of the Oldham ring 160 for almost linear motion in the radial direction cross each other, the second key 163 is moved by the orbiting scroll 150. Movement of the orbiting scroll 150 in the direction of rotation can be minimized. Through this, the Oldham ring 160 appropriately limits the rotation of the orbiting scroll 150, thereby maintaining compressor efficiency.

Referring to FIGS. 3 to 5 , the cross-sectional area of the first key portion 1631 may be smaller than that of the second key portion 1632 . For example, the diameter of the first key portion 1631 is defined as the short axis length of the second key portion 1632, that is, the distance between both transverse side surfaces 1632a of the second key portion 1632. It may be formed smaller than the radial side length (L2). Accordingly, the overall weight of the Oldham ring 160 can be reduced by minimizing the weight of the first key portion 1631 . However, in some cases, the cross-sectional area of the first key portion 1631 may be greater than or equal to the cross-sectional area of the second key portion 1632. In this case, the radial side length L2 of the second key portion 1632 is made small or the outer diameter of the first key portion 1631 is increased. The former can further lower the weight of the Oldham ring 160, while the latter Reliability can be improved by increasing the rigidity of the first key portion 1631.

Although not shown in the drawings, the first key portion 1631 may be formed in a hollow hollow shape. In this case, the Oldham ring 160 can be lightened by further reducing the weight of the second key 163 .

Referring to FIGS. 3 to 5 , the second key portion 1632 may be formed in a long rectangular shape in a radial direction. For example, the second key portion 1632 is formed in a rectangular box shape when projected in the axial direction as a whole, but has a transverse side surface (hereinafter, a side surface orthogonal to the radial direction in the transverse direction is defined as a transverse side surface) The length (L1) of (1631a) may be formed longer than the length (L2) of the radial side surface (1632b). Accordingly, the contact area between the second key portion 1632 of the second key 163 and the second key groove 1511 is widened to lower the surface pressure transmitted from the second key 163 to the second key groove 1511, Through this, wear of the second key 163 of the Oldham ring 160 or the second key groove 1511 of the orbiting scroll 150 can be suppressed.

Both transverse side surfaces 1632a of the second key portion 1632 may be formed flat to be parallel to each other, and both radial side surfaces 1632b may be formed flat to be parallel to each other. Accordingly, the second key 163 including the second key portion 1632 can be easily manufactured by easily forming the first key portion 1631 .

Although not shown in the drawings, the second key portion 1632 need not be formed parallel to both transverse side surfaces 1632a and both radial side surfaces 1632b. For example, other side surfaces of the second key portion 1632 except for one transverse side surface 1632a of the second key portion 1632 that contacts the transverse side surface 1511a of the second key groove 1511 during operation of the compressor are flat. Alternatively, it may be formed in various ways such as a curved surface.

Both transverse side surfaces 1632a of the second key portion 1632 and both transverse side surfaces 1511a of the second key groove 1511 facing the same may be spaced apart from each other. For example, between both transverse side surfaces 1632a of the second key portion 1632 and both transverse side surfaces 1511a of the second key groove 1511 facing the same, a sliding gap G2 of a preset length may be formed. can Accordingly, the second key 163 slides in the radial direction with respect to the second key groove 1511, so that the orbiting scroll 150 coupled to the rotational shaft 125 can induce a rotational motion while suppressing rotation.

The sliding gap G2 may be formed to be significantly smaller than a width through which oil may flow, for example, a transverse width of the second key 163. As described above, the sliding interval G2 may be greater than or equal to the rotational interval G1. Accordingly, the second key 163 of the Oldham ring 160 can smoothly slide in the second key groove 1511 and suppress the rotation of the orbiting scroll 150.

The Oldham ring according to the present embodiment as described above has the following effects. 6A and 6B are schematic diagrams shown in FIG. 3 to explain the correspondence between the second keyway and the second key, and FIG. 7 is a cross-sectional view shown in FIG. 1 to explain the oil supply around the Oldham Ring.

6A and 6B, before the operation of the compressor, the second key (more precisely, the second key part) 163 of the Oldham ring 150 is in a parallel state with the second keyway 1511 of the orbiting scroll 150. On the other hand, during operation of the compressor, the second key portion 1632 constituting the second key 163 of the Oldham ring 160 does not maintain a parallel state with the second key groove 1511 of the orbiting scroll 150. .

That is, referring to FIG. 6A , before the operation of the compressor, the second radial center line CL2 passing through the radial center of the second key portion 1632 is the first radial center line passing through the radial center of the second key groove 1511 ( CL1) may be formed on the same line or parallel to the radial center line CL of the ring body 161.

On the other hand, referring to FIG. 6B, while the compressor is operating, the first radial center line CL1 and the second radial center line CL2 maintain almost the same line or parallel state, but the radial center line of the ring body 161 ( CL) is twisted and intersects.

In other words, the orbiting scroll 150 eccentrically coupled to the rotation shaft 125 tends to rotate by receiving the rotational force of the rotation shaft 125, whereas the Oldham ring 160 has a main frame to which the first key 162 is fixed ( 130), the second keys 163 are slidably coupled to the orbiting scrolls 150 to perform rotational motions, and tend to perform linear motions in directions orthogonal to each other.

As a result, the direction of rotational movement of the orbiting scroll 150 and the direction of linear movement of the Oldham ring 160 intersect with each other, and one transverse side surface 1632a of the second key portion 1632 forming a part of the second key 163 and One transverse side surface 1511a of the second key groove 1511 facing this is brought into close contact with each other.

At this time, if the second key 163 including the second key part 1632 is fixed to the ring body 161 as in the above-mentioned patent documents, the second radial center line CL2 of the second key part 1632 is The second key portion 1632 is twisted with respect to the second key groove 1511 so as to intersect the first radial center line CL1 of the second key groove 1511 . Then, line contact is generated between the transverse side surface 1632a of the second key portion 1632 and the transverse side surface 1511a of the second key groove 1511, which will be described later.

However, as in the present embodiment, the first key portion 1631 forming a part of the second key 163 is rotatably inserted in the key receiving groove 1612 of the ring body 161, that is, the second key 163 ) is inserted into the ring body 161 in a free state, the second key 163 actively embraces the rotational motion of the orbiting scroll 150.

Then, the rotation angle allowed by the range determined by the second key 163 along the direction in which the orbiting scroll 150 rotates, that is, the sliding distance G2 between the second key unit 1632 and the second key groove 1511 ( α) is rotated. Then, even if the second radial center line CL2 of the second key portion 1632 is distorted with respect to the radial center line CL of the ring body 161, the first radial center line CL1 of the second key groove 1511 will remain in equilibrium.

Then, the second key 163 maintains a state in which one transverse side surface 1632a of the second key portion 1632 is in surface contact with one transverse side surface 1511a of the second key groove 1511 facing it. will make a turn Through this, the Oldham ring 160 can prevent friction loss and wear between the second key 163 and the second key groove 1511 in advance while suppressing the rotational motion of the orbiting scroll 150.

In this way, when the orbiting scroll 150 and the Oldham ring 160 are made of the same material, the ring body 161 of the Oldham ring 160 is made of the same material as the orbiting scroll 150, so that the Oldham ring 160 While the weight of the second key 163 is formed of a material different from that of the ring body 161, frictional loss between the orbiting scroll 150 and the Oldham ring 160 can be suppressed.

In addition, as the second key 163 slidingly coupled to the orbiting scroll 150 is rotatably coupled to the ring body 161, the second key 163 corresponds to the orbiting scroll 150 within the permitted range. While rotating within, the second key portion 1632 of the second key 163 maintains a surface contact state with the second key groove 1511 of the orbiting scroll 150. Through this, the surface pressure between the Oldham ring 160 and the orbiting scroll 150 is lowered to further reduce frictional loss and wear.

In addition, as a rotation interval G1 is formed between the key receiving groove 1612 of the ring body 161 and the first key portion 1631 of the second key 163, the oil around the Oldham ring 160 rotates. It can quickly flow between the ring body 161 and the second key 163 through the gap G1. Accordingly, an oil film is formed between the key receiving groove 1612 of the ring body 161 and the first key portion 1631 of the second key 163 to reduce friction loss between the ring body and the second key, and at the same time, turning Frictional loss and wear can be further reduced by lowering the surface pressure between the scroll 150 and the Oldham ring. (See Fig. 7)

In addition, when the ring body 161 and the second key 163 constituting the Oldham ring 160 are manufactured and assembled, the tolerance for the assembly structure of the ring body 161 and the second key 163 is increased and The dam ring 160 can be easily manufactured, and through this, the manufacturing cost of the Oldham ring 160 can be reduced while reliability can be increased.

Meanwhile, the case where there is another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiment, the outer surfaces of the second key portion and the first key portion constituting the second key are formed flat, but in some cases, an oil supply passage may be formed on the outer surfaces of the second key portion and the first key portion.

8 and 9 are perspective views and cross-sectional views showing another embodiment of the Oldham ring, and FIGS. 10 and 11 are perspective views and cross-sectional views showing another embodiment of the second key of the Oldham ring.

Referring to FIGS. 8 to 11 , the Oldham ring 160 according to the present embodiment may include a ring body 161 , a first key 162 and a second key 163 . Since the ring body 161 and the first key 162 are formed almost identically to those of the foregoing embodiment, a detailed description thereof is replaced with the description of the foregoing embodiment.

Also, the second key 163 may include a first key portion 1631 and a second key portion 1632 . The first key section 1631 and the second key section 1632 are generally similar to the first key section 1631 and the second key section 1632 in the foregoing embodiment. For example, the first key portion 1631 according to the present embodiment is formed in a cylindrical cross-sectional shape extending in the axial direction from the second key portion 1632, and the second key portion 1632 is formed in a rectangular cross-sectional shape when projected in the axial direction. It can be.

However, an oil supply passage 1635 may be further formed in the second key 163 according to the present embodiment to guide the oil around the Oldham ring 160 to the rotation interval G1 or sliding interval G2. For example, a first supply supply passage 1635a may be formed in the first key part 1631, and a second supply supply passage 1635b may be formed in the second key part 1632.

Referring to FIGS. 8 and 9 , the first oil supply passage 1635a may be formed in a groove shape depressed by a preset depth on the outer circumferential surface of the first key part 1631 . The first oil supply passage 1635a may be formed to extend in an axial direction, a spiral direction, or an oblique direction along an outer circumferential surface of the first key portion 1631 and terminate between a lower end and an upper end of the first key portion 1631 .

The second oil supply passage 1635b may be formed in a recessed groove shape by a predetermined depth on the outer circumferential surface of the second key portion 1632, more precisely, on the transverse side surface 1632a of the second key portion 1632. The second oil supply passage 1635b may extend axially or obliquely from the middle of the transverse side surface 1632a in the radial direction to terminate between the lower end and the upper end of the second key portion 1632 .

The second supply supply passage 1635b may be connected to the first supply supply passage 1635a. In other words, the lower end of the second supply supply passage 1635b may be directly connected to the upper end of the first supply supply passage 1635a, or may be formed with a slight gap therebetween.

For example, the lower end of the second key part 1632 is wider than the upper end of the first key part 1631, so that there is a stepped surface between the lower end of the second key part 1632 and the upper end of the first key part 1631 (unsigned). ) is formed, a connection groove (not shown) connecting the second supply supply passage 1635b to the first supply supply passage 1635a may be formed to extend in the transverse direction on the stepped surface. However, the second supply supply passage 1635b may be connected to the first supply supply passage 1635a without separately forming a connection groove. This embodiment shows an example in which the second supply supply passage is connected to the first supply supply passage without a connection groove.

Although not shown in the drawings, only one oil supply passage may be formed from among the first oil supply passage 1635a and the second oil supply passage 1635b. Even in this case, a certain amount of oil may be supplied to the rotation interval G1 and the sliding interval G2 as in the above-described embodiment.

As described above, as the first key portion 1631 has the first oil supply passage 1635a and the second key portion 1632 has the second oil supply passage 1635b, the oil pooled around the Oldham ring 160. The silver can be smoothly introduced into the rotation interval G1 between the first key portion 1631 and the key receiving groove 1612 and the sliding interval G2 between the second key portion 1511 and the second key portion 1632 .

Accordingly, the oil flowing into the rotational interval G1 forms an oil film between the outer circumferential surface of the first key part 1631 and the inner circumferential surface of the key receiving groove 1612 so that the first key part 1631 is the center of the key receiving groove 1612. It can rotate with almost no friction inside. In addition, the oil flowing into the sliding gap G2 forms an oil film between the outer surface (lateral side surface) of the second key portion 1632 and the inner surface (lateral side surface) of the second key groove 1511 to form the second key portion (lateral side surface). 1632) can perform linear motion in the radial direction without almost friction inside the second keyway 1511.

10 and 11, the second oil supply passage 1635b is the same as in the previous embodiment, but the first oil supply passage 1635a is formed as a hole penetrating the inside of the first key part 1631. may be In this case, the first supply supply passage 1635a may be inclined so that both first supply supply passages 1635a cross each other. Although not shown in the drawing, the first supply oil passage 1635a may be formed in an axial direction.

As described above, even when the first oil supply passage 1635a is formed as a hole penetrating the inside of the first key portion 1631, its effect is to pass through the outer circumferential surface of the first key portion 1631 as in the above-described embodiment. It may be similar to the case of being formed as a groove. Even in this case, the oil around the Oldham ring 160 passes through the first oil supply passage 1635a and then is transferred to the second oil supply passage 1635b to lubricate the rotation interval G1 and the sliding interval G2, respectively. do.

Although not shown in the drawings, the fuel supply passage 1635 may be formed on the opposite surface to which the second key 163 comes into contact. For example, a first oil supply passage 1635a may be formed on the inner circumferential surface of the key receiving groove 1612, and a second oil supply passage 1635b may be formed on the transverse side surface 1511a of the second key groove 1511, respectively. there is. As described above, even when the oil supply passage 1635 is formed on the opposite surface to which the second key 163 comes into contact, its effect may be similar to that of the above-described embodiment. Of course, even in this case, only one oil supply passage may be formed.

In this way, in the Oldham ring 160 according to the present embodiment, a wide and thick oil film can be formed on the second key 163 and the contact surface or friction surface where the second key 163 contacts, and through this, the contact surface or It can reduce friction loss and wear on the friction surface.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiment, the second oil supply passage is formed on the lateral side of the second key portion and the first oil supply passage is formed on the outer circumferential surface of the first key portion, respectively, but in some cases, the oil supply passage is formed only in the first key portion. may be

12 and 13 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring.

12 and 13, the Oldham ring 160 according to the present embodiment includes a ring body 161, a first key 162 and a second key 163, and includes the ring body 161 and the second key 161. 1 key may be formed in the same way as in the above-described embodiment.

Also, the second key 163 is almost similar to the second key 163 in the above-described embodiments. For example, the second key 163 may include a first key portion 1631 and a second key portion 1632 . However, in this embodiment, the oil supply passage may be formed only in the first key part 1631.

Specifically, in the above-described embodiments, the first supply supply passage 1635a is formed in the first key part 1631 and the second supply supply passage 1635b is formed in the second key part 1632, respectively. In , the first supply supply passage 1635a is formed in the first key part 1631, but the second supply supply passage 1635b may be excluded from the second key part 1632.

In this case, the first oil supply passage 1635a is a portion covered by the second key portion 1632, that is, a decut ( D-Cut) can be formed respectively.

As described above, when the first oil supply passage 1635a is formed in a decut shape on both sides of the first key portion 1631 in the radial direction, a kind of oil storage space is formed between the first oil supply passage and the inner circumferential surface of the key receiving groove 1612. can be formed. Then, the oil around the Oldham ring 160 can flow into and be stored in the storage space formed by the first oil supply passage 1635a.

In addition, the oil stored in the storage space continuously lubricates between the first key portion 1631 and the key receiving groove 1612 while the compressor is operating, and at the same time, a certain amount of oil can be retained due to viscosity even when the compressor is stopped. Then, when the compressor is restarted, the oil stored in the first oil supply passage (1635a) lubricates between the first key part (1631) and the key receiving groove (1612), so that the second key (163) is against the ring body (161). It can rotate smoothly. Then, even at the beginning of operation of the compressor, the transverse side surface 1632a of the second key portion 1632 constituting a part of the second key 163 is the transverse side surface 1511a of the second key groove 1511 provided in the orbiting scroll 150 ), friction loss and wear can be reduced.

Although not shown in the drawing, the first oil supply passage 1635a is formed on the transverse side of the first key portion 1631, or is formed on the radial side and the transverse side of the first key portion 1631, respectively. It could be.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiment, the second key portion is formed in the shape of a solid rectangular bar, but in some cases, a recessed oil storage groove may be further formed on the upper surface of the second key portion.

14 and 15 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring.

14 and 15, the Oldham ring 160 according to the present embodiment includes a ring body 161, a first key 162 and a second key 163, and includes the ring body 161 and the second key 161. 1 key 162 may be formed in the same way as in the above-described embodiment. The second key 163 is almost similar to the second key 163 in the above-described embodiments. For example, the second key 163 includes a second key portion 1632 and a first key portion 1631, and a first oil supply passage 1635a is formed on an outer circumferential surface of the first key portion 1631. ) The second supply passage (1635b) may be formed on the transverse side of each.

However, a low oil groove 1636 having a preset depth may be recessed on the upper surface of the second key portion 1632 according to the present embodiment. The cross-sectional area of the reservoir groove 1636 may be larger than the cross-sectional area of the second oil supply passage 1635b.

The storage groove 1636 may be in communication with the second oil supply passage 1635b. For example, a communication groove 1636a may be formed on an upper edge of the second key portion 1632 . The communication groove 1636 connects the second oil supply passage 1635b and the reservoir groove 1636, and is formed to be recessed by a predetermined depth from the upper edge of the second key part 1632, as shown in FIG. 14, or the upper half It may be formed by penetrating in the transverse direction. However, when the upper surface of the second key portion 1632 does not or intermittently contact the upper surface of the second key groove 1511, the aforementioned communication groove 1636a may be excluded.

As described above, when the oil storage groove 1636 is formed on the upper surface of the second key portion 1632, the oil around the Oldham ring 160 flows through the first oil supply passage 1635a and the second oil supply passage ( 1635b), and can be introduced into the storage groove 1636 through the communication groove 1636a and stored therein.

The oil stored in the storage groove 1636 is supplied between the transverse side surface 1632a of the second key portion 1632 and the transverse side surface 1511a of the second key groove 1511 facing it during the operation of the compressor, and the sliding distance G2 ), while retaining a certain amount of oil even when the compressor is stopped. Then, when the compressor is restarted, the oil stored in the oil storage groove is quickly supplied between the second key portion 1632 and the key receiving groove 1612 to lubricate the sliding gap G2. Then, friction loss and wear between the second key part 1632 and the second key groove 1511 can be reduced even in the initial stage of operation of the compressor.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiment, the second key is coupled to the ring body in a free state, but in some cases, the second key may be constrained to the ring body in the axial direction.

16 and 17 are perspective and cross-sectional views showing another embodiment of the second key of the Oldham ring.

Referring to FIGS. 16 and 17 , the Oldham ring 160 according to the present embodiment may include a ring body 161 , a first key 162 and a second key 163 . Since the ring body 161 and the first key 162 are formed almost identically to those of the foregoing embodiment, a detailed description thereof is replaced with the description of the foregoing embodiment.

The second key 163 may include a first key portion 1631 and a second key portion 1632 . The first key section 1631 and the second key section 1632 are generally similar to the first key section 1631 and the second key section 1632 in the foregoing embodiment. For example, the first key portion 1631 according to the present embodiment is formed in a cylindrical cross-sectional shape extending in the axial direction from the second key portion 1632, and the second key portion 1632 is formed in a rectangular cross-sectional shape when projected in the axial direction. It can be. Accordingly, the second key 163 is rotatably coupled to the key receiving groove 1612 so that the second key portion 1632 constituting the second key 163 is centered around the first key portion 1631 during operation of the compressor. While rotating with respect to the dam ring 160, it is possible to maintain surface contact with the second key groove 1511.

However, a key restraining part 1637 may be further provided at the lower end of the first key part 1631 according to the present embodiment, that is, at the opposite end of the second key part 1632 . For example, the key restraining portion 1637 may include a flange screw having a head portion such as a flange and screwed to the first key portion 1631 .

In this case, a screw fastening groove 1631a is formed in the axial direction at the lower end of the first key part 1631, and the head of the flange screw constituting the key restraining part 1637 is axial at the other end of the key receiving groove 1612. A screw locking jaw 1612a supported in the direction may be formed.

As described above, when the key restraining part 1637 is provided at the lower end of the first key part 1631, the second key 163 rotates with respect to the ring body 161, but its axial movement may be restricted. For example, in the second key 163 according to the present embodiment, the upper end of the first key part 1631 is constrained in the first axial direction by the second key part 1632, and the lower end of the first key part 1631 is the key. It is constrained in the second axial direction by the restraining portion 1637 . Then, when assembling the Oldham ring 160, the separation of the second key 163 from the ring body 161 can be suppressed, so that the Oldham ring 160 can be easily assembled.

In addition, it is possible to prevent the second key 163 from colliding with the orbiting scroll 150 by suppressing the jumping of the second key 163 from the Oldham ring 160 during operation of the compressor. Through this, the second key 163 formed of a relatively hard material collides with the orbiting scroll 150 formed of a relatively soft material so that the second keyway 1511 of the orbiting scroll 150 is worn out or abnormal noise is generated. can suppress

Although not shown in the drawing, the key restraint part 1637 may extend from the lower end of the first key part 1631 as a single body. In this case, a key support surface may be formed at the lower end of the key receiving groove 1612 to cover the key receiving groove 1612, and a key restraining groove may be formed in a rectangular shape to correspond to the key restraining part at the center of the key receiving surface. Accordingly, the key restraint part 1637 can rotate after passing through the key restraint groove and be supported in the axial direction by being caught on the surface opposite to the key support surface. In this case, the manufacturing cost can be lowered by reducing the number of parts compared to the case where the key restraining part 1637 is formed by a separate fastening member such as a flange screw.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiments, the second key portion is formed to be long in the radial direction, but in some cases, the radial direction and the lateral direction may be the same or may be formed to be longer in the lateral direction.

18 is a perspective view showing another embodiment of the second key of the Oldham ring.

Referring to FIG. 18 , the Oldham ring 160 according to the present embodiment may include a ring body 161 , a first key 162 and a second key 163 . Since the ring body 161 and the first key 162 are formed almost identically to those of the above-described embodiments, specific descriptions thereof are replaced with those of the above-described embodiments.

The second key 163 may include a first key portion 1631 and a second key portion 1632 . The first key section 1631 and the second key section 1632 are generally similar to the first key section 1631 and the second key section 1632 in the foregoing embodiment. For example, the first key portion 1631 according to the present embodiment may be formed in a cylindrical cross-sectional shape extending in an axial direction from the second key portion 1632, and the second key portion 1632 may be formed in a rectangular cross-sectional shape.

However, the second key portion 1632 according to the present embodiment may be formed in a square or rectangular shape when projected in an axial direction, but may have a longer lateral length than a radial length. In this embodiment, an example in which the second key portion 1632 has a square shape will be mainly described.

The first key portion 1631 extends in an axial direction from the center of the second key portion 1632 and is formed in a cylindrical shape, and the second key portion 1632 has a lateral side length L1 and a radial side length L2. can be formed in the same way. Accordingly, the second key 163 is rotatably coupled to the key receiving groove 1612 so that the second key portion 1632 constituting the second key 163 is centered around the first key portion 1631 during operation of the compressor. While rotating with respect to the dam ring 160, it is possible to maintain surface contact with the second key groove 1511.

Even when the second key portion 1632 is formed in a square shape as described above, the lateral side surface of the second key portion 1632 may be in surface contact with the lateral side surface of the second key groove 1511 as described above. Accordingly, the radial length of the second key portion 1632 is reduced while reducing frictional loss and wear between the second key and the second keyway 1511, so that the entire Oldham ring 160 including the second key 163 is formed. weight can be reduced. Through this, the centrifugal force of the orbiting scroll 150 including the Oldham ring 160 can be reduced to increase motor efficiency.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiments, the second key is formed as a single body, but in some cases, the second key may be integrally coupled by assembling the second key unit and the first key unit.

19 is a cross-sectional view showing another embodiment of the second key of the Oldham ring.

Referring to FIG. 19 , the Oldham ring 160 according to the present embodiment may include a ring body 161 , a first key 162 and a second key 163 . Since the ring body 161 and the first key 162 are formed almost identically to those of the above-described embodiments, specific descriptions thereof are replaced with those of the above-described embodiments.

However, the second key 163 includes the first key portion 1631 and the second key portion 1632, but may be formed by combining the second key portion 1632 with the first key portion 1631. Even in this case, the first key portion 1631 and the second key portion 1632 may be formed of the same material.

However, when the first key section 1631 and the second key section 1632 are assembled as in the present embodiment, it may be preferable that the first key section 1631 and the second key section 1632 are formed of different materials. there is. For example, the first key unit 1631 may be formed of the same material as the orbiting scroll 150, that is, aluminum, and the second key unit 1632 may be formed of a material different from that of the orbiting scroll 150, that is, cast iron. . Accordingly, the second key 163 may be formed by press-fitting the first key portion 1631 and the second key portion 1632 or by using a method such as aluminum die casting.

Even in this case, the first key part 1631 is rotatably inserted into the key receiving groove 1612 of the ring body 161 at a rotational interval G1 and coupled, and the second key part 1632 is connected to the orbiting scroll 150 It can be coupled by slidingly inserted into the second key groove 1511 at a sliding interval G2. Accordingly, as the second key 163 rotates with respect to the ring body 161 during operation of the compressor as in the above-described embodiments, the second key portion 1632 constituting the second key 163 forms the second key groove ( 1511) to reduce friction loss and wear.

As described above, the first key portion 1631 and the second key portion 1632 constituting the second key 163 are formed of different materials, and the first key portion 1631 is made of aluminum, so that the second key ( 163) can be further reduced in weight. Through this, the overall weight of the Oldham ring 160 is reduced, and motor efficiency can be further improved.

Meanwhile, another embodiment of the Oldham ring is as follows.

That is, in the above-described embodiments, the second key is formed as a single body, but in some cases, the second key may be separated into the first key and the second key and the second key may be rotatably assembled to the first key. there is.

20 and 21 are an exploded perspective view and an assembled cross-sectional view showing another embodiment of the Oldham ring.

20 and 21 , the Oldham ring 160 according to the present embodiment may include a ring body 161, a first key 162 and a second key 163. Since the ring body 161 and the first key 162 are formed almost identically to those of the above-described embodiments, specific descriptions thereof are replaced with those of the above-described embodiments. However, part of the second key 163 may be integrally formed or assembled to the ring body 161 unlike the above-described embodiments.

Specifically, the second key 163 according to the present embodiment may include a first key portion 1631 and a second key portion 1632 .

The first key portion 1631 and the second key portion 1632 may be rotatably assembled to each other. For example, the first key portion 1631 may be formed in a cylindrical shape with a circular outer circumferential surface, and the second key portion 1632 may be formed in a square ring shape with a key receiving groove 1638 having a circular inner circumferential surface in the center thereof. there is.

The first key portion 1631 is monolithically extended from the second expansion portion of the ring body 161 toward the orbiting scroll 150 and is rotatably coupled to the key receiving groove 1638 of the second key portion 1632. The second key unit 1632 can be coupled to the second key groove 1511 of the orbiting scroll 150 by sliding in the radial direction.

A rotational gap G1 is formed between the outer circumferential surface of the first key portion 1631 and the inner circumferential surface of the second key portion 1632 facing it (ie, the inner circumferential surface of the key receiving groove), and the lateral side surface of the second key portion 1632 A sliding gap G2 may be formed between 1632a and the transverse side surface 1511a of the second key groove 1511. The rotation interval G1 may be formed equal to or smaller than the sliding interval G2 as in the above-described embodiments.

As described above, even when the first key portion 1631 and the second key portion 1632 constituting the second key 163 are rotatably coupled to each other, the second key 163 during operation of the compressor as in the above-described embodiments As the second key portion 1632 forming the ring body 161 rotates with respect to the first key portion 1631 forming the second key portion 163, the transverse side surface 1632a of the second key portion 1632 forming the second key portion 163 It comes into surface contact with the transverse side surface 1511a of the second key groove 1511, thereby reducing frictional loss and wear.

Furthermore, as in the present embodiment, the second key portion 1632 and the first key portion 1631 constituting the second key 163 are formed of different materials, and the first key portion 1631 is a ring body made of aluminum. As it is integrally formed with 161, the weight of the second key 163 including the first key portion 11631 and the second key portion 1632 can be further reduced. Through this, the overall weight of the Oldham ring 160 is reduced, and motor efficiency can be further improved.

Meanwhile, in the foregoing embodiments, the main frame 130 has been described focusing on an example formed of a material different from that of the Oldham ring 160 or the orbiting scroll 150, but in some cases, the main frame 130 may also come It may be formed of the same material as the dam ring 160 or the orbiting scroll 150. In this case, the first key 162 of the Oldham ring 160 can be coupled to the main frame 130 and slidably coupled to the Oldham ring 160 in the same manner as the second key 163 described above. A detailed description of this will be replaced with the description of the above-described embodiment.

In addition, when the Oldham ring 160 is integrally formed, the previously described liner 170 may be inserted into the first key groove (not shown) of the main frame 130 . A detailed description thereof is also replaced by a description of the above-described embodiment.

110: casing 110a: inner space
110b: upper space (discharge space) 110c: middle space (oil separation space)
110d: lower space (low oil space) 111: cylindrical shell
112: upper cap 113: lower cap
115: refrigerant suction pipe 116: refrigerant discharge pipe
118: subframe 120: drive motor
121 stator 1211 stator core
1212: stator coil 122: rotor
1221: rotor core 1222: permanent magnet
125: axis of rotation 1251: eccentric
1255: oil supply hole 126: oil pickup
130: main frame 131: main flange part
1311: second discharge passage groove 132: shaft support projection
1321: shaft support hole 140: fixed scroll
141: fixed end plate 1411: inlet
1412: discharge port 142: fixed side wall
1421: first discharge passage groove 143: fixed wrap
145: discharge valve 150: orbiting scroll
151: turning head plate part 1511: second keyway
1511a: transverse side 152: rotating shaft coupling part
153: turning lap 160: Oldham ring
161: ring body 1611: extension
1611a: first extension 1611b: second extension
1612: key receiving groove 1612a: screw locking jaw
162: first key 163: second key
1631: first key part 1631a: screw fastening groove
1632: second key portion 1632a: transverse side
1632b: radial side 1635: oil passage
1635a: first supply passage 1635b: second supply passage
1636: low oil groove 1636a: communication groove
1637: key restraint 1637a: flange screw
1638: key receiving groove CL: radial center line of ring body
CL1: first radial centerline CL2: second radial centerline
G1: Rotation interval G2: Sliding interval
L1: Transverse side length L2: Radial side length
V: compression chamber

Claims (20)

A plurality of scrolls including orbiting scrolls that are engaged with each other and at least one of the scrolls is coupled to a rotation shaft to perform a orbital motion; and
an Oldham ring that is slidably coupled to a keyway provided in the orbiting scroll and induces orbital movement of the orbiting scroll;
The Oldham Ring,
a ring body formed in an annular shape and provided with at least one key receiving groove; and
One end is provided with a first key unit inserted into the key receiving groove, and the other end includes at least one key having a second key unit inserted into the key groove,
The first key part,
It is rotatably inserted in the key receiving groove,
At least one of the outer circumferential surface or inner surface of the first key unit and the inner circumferential surface of the key receiving groove is formed with a first oil supply passage in a straight line or an oblique line along the axial direction,
A second oil supply passage is formed on a transverse side surface of the second key portion that is in sliding contact with the key groove,
The scroll compressor wherein the first oil supply passage and the second oil supply passage communicate with each other. According to claim 1,
A scroll compressor provided with a rotation interval spaced apart in a radial direction between an inner circumferential surface of the key receiving groove and an outer circumferential surface of the first key unit. According to claim 2,
A sliding gap spaced apart in a transverse direction is provided between the second key portion and the key groove,
The rotation interval is
A scroll compressor that is less than or equal to the sliding distance. According to claim 1,
At least one of the inner circumferential surface of the key receiving groove and the outer circumferential surface of the first key unit is formed in a circular cross-sectional shape. According to claim 1,
The second key unit is a scroll compressor in which both transverse side surfaces are formed in parallel. According to claim 5,
Wherein the second key portion is formed in a rectangular cross-sectional shape in which a radial length is longer than a lateral length. According to claim 5,
Wherein the second key portion has a radial length equal to or smaller than a lateral length of the scroll compressor. According to claim 1,
The first key unit and the second key unit are formed as a single scroll compressor. According to claim 1,
The first key unit is inserted into and coupled to the second key unit. According to claim 9,
The scroll compressor of claim 1 , wherein the first key portion is formed of a harder material than the second key portion. According to claim 1,
The outer circumferential surface of the first key unit is a scroll compressor formed in a smooth tube shape. delete delete According to claim 1,
Oil supply passages are formed in the second key portion and the first key portion, respectively;
An end surface of the second key portion is formed with a storage groove recessed to a predetermined depth,
The oil supply passage is a scroll compressor in communication with the oil storage groove. According to claim 1,
A key binding portion extending in a radial direction is further provided at an opposite end of the second key portion among both ends in the axial direction of the first key portion,
The key binding unit,
A scroll compressor formed larger than the inner diameter of the key receiving groove. The method of any one of claims 1 to 11 and 14 to 15,
The ring body is formed of the same material as the orbiting scroll,
The key is a scroll compressor formed of a different material from the ring body. delete delete delete delete

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