KR102619911B1 - Compressor - Google Patents

Abstract

The compressor starts. A compressor according to an embodiment of the present invention provides a compressor that can stably retain oil by supplying oil to the area of the suction chamber or back pressure chamber.

Description

Compressor {Compressor}

The present invention relates to a compressor in which the movement path of the oil discharged from the discharge part is changed, and more specifically, to a compressor in which the oil residual amount is improved by forming a flow path so that oil can always be supplied to the suction chamber and the back pressure chamber.

In general, a compressor used in an air conditioning system sucks refrigerant that has completed evaporation from an evaporator, changes it into a high temperature and high pressure state that is easy to liquefy, and delivers it to the condenser. The compressor operates to compress the refrigerant moved through the evaporator.

There are two types of compressors: a reciprocating type, which performs compression while the drive source for compressing the refrigerant reciprocates, and a rotary type, which performs compression while rotating.

The reciprocating type includes a crank type that transmits the driving force of the drive source to a plurality of pistons using a crank, a swash plate type that transmits the driving force of the drive source to a rotating shaft on which a swash plate is installed, and a wobble plate type that uses a wobble plate.

There are two types of rotary types: the vane rotary type, which uses a rotating rotary shaft and vanes, and the scroll type, which uses a rotating scroll and a fixed scroll.

The scroll compressor has advantages such as high efficiency, low noise, low vibration, and light weight compared to other types of compressors. In particular, it is suitable when equipped with an inverter and can automatically prevent overpressure when liquid refrigerant or foreign substances are injected into the compressor. It has structural characteristics.

Due to these advantages, the scope of use of scroll compressors has expanded to include various cooling capabilities, and for example, they are used in a variety of applications such as room air conditioners and commercial air conditioners as well as residential air conditioners.

The scroll compressor is provided with two scrolls that are engaged with each other and can rotate relatively, and the two scrolls are composed of a fixed scroll and an orbiting scroll. The fixed scroll and the orbiting scroll have a circular end plate and a spiral element (wrap or spiral element) protruding from the circular end plate.

The fixed scroll and each spiral element of the orbiting scroll are arranged to be interlocked with each other, and as the orbiting scroll rotates relative to the fixed scroll, the volume between the spiral element of the orbiting scroll and the spiral element of the fixed scroll moves while changing. More fluid pockets are formed.

As the orbiting scroll progresses, the fluid pocket moves to the discharge port of the housing and its volume decreases, and the refrigerant fluid in the fluid pocket is compressed and discharged through the discharge port.

The orbiting scroll of the scroll compressor is driven by a drive shaft, and the drive shaft is driven by an external power source. The orbiting scroll is installed eccentrically with respect to the drive shaft via an eccentric bush, and when the drive mechanism is operated, the orbiting scroll rotates eccentrically with respect to the center of the drive shaft by rotation of the drive shaft. Bearings are provided at the rotational contact parts of the drive shaft, eccentric bush, and orbiting scroll to support rotation.

A compressor operated in this way must be provided with appropriate lubrication to ensure smooth operation and durability, and for this lubrication, the refrigerant fluid contains a trace amount of oil.

The refrigerant fluid containing the oil is configured to lubricate the drive shaft, eccentric bush, and orbiting scroll while moving. The scroll compressor discharges refrigerant compressed by a fluid pocket, and the compressed refrigerant thus discharged contains oil for lubrication.

The scroll compressor separates the oil from the oil-containing compressed refrigerant and then returns the separated oil to the low pressure part in the housing, thereby increasing the heat exchange efficiency of the discharged compressed refrigerant and minimizing oil waste. The structure is in place.

The conventional scroll compressor configured in this way had a problem in that oil was not sufficiently supplied to the drive mechanism because it was located in the direction of gravity (upper part of the drive shaft) with respect to the drive shaft.

In this case, friction loss and heat generation due to the drive shaft and rotation of the drive shaft increase, and the lifespan of the drive mechanism is shortened.

In addition, when operating at low load with a small amount of oil circulation, there was a problem in that the amount of oil supplied to the back pressure chamber (not shown) of the scroll compressor was reduced. In this case, the pressure in the back pressure chamber becomes lower than the predetermined level, and various sliding parts are damaged due to failure to lubricate smoothly, which creates a need for countermeasures.

Republic of Korea Patent Publication No. 10-2017-0032094

Embodiments of the present invention are intended to provide a compressor capable of maintaining a constant oil residual amount by stably supplying oil required for lubrication of the suction chamber and back pressure chamber of a scroll compressor.

The compressor according to the first embodiment of the present invention includes a front housing in which a suction chamber is formed and a driving part for generating a driving force therein; a center housing coupled to face the front housing and having a back pressure chamber formed therein; a turning scroll that receives rotational force from the driving unit on one side facing the center housing; a fixed scroll installed so that the orbiting scroll can rotate and forming a compression chamber together with the orbiting scroll; a rear housing having a discharge chamber configured to accommodate refrigerant discharged from the compression chamber; and a flow path is formed so that a portion of the oil contained in the refrigerant discharged to the discharge chamber is supplied at different flow rates toward the suction chamber and the back pressure chamber, the flow path comprising a first flow path communicating with the discharge chamber, and a second flow path communicating with the first flow path, one end of which is open in the center housing, and the other end of which is open toward the back pressure chamber; and a second flow path communicating with the second flow path and extending upward along the circumferential direction of the center housing. It includes a third flow path and a fourth flow path, one end of which is connected to the third flow path and the other end of which is open toward the suction chamber, and the second flow path and the fourth flow path are located in the center housing facing the fixed scroll. is formed on the opposing surface of
The third flow path has a smaller cross-sectional area than the second flow path and the fourth flow path.
A sealing member for sealing oil moving along the fourth flow path from the first flow path is interposed between the center housing and the orbiting scroll, wherein the sealing member includes: a first sealing portion in close contact with the center housing; One side is in close contact with the first sealing portion, and the other side is in close contact with the orbiting scroll, and includes a second sealing portion made of a different material from the first sealing portion.
The first sealing portion is formed with an insertion protrusion inserted into the opening of the second to fourth flow passages.
A first pressure reducing part for reducing the pressure of oil moving to the second flow path is inserted into the first flow path.
A second pressure reducing part for reducing the pressure of oil moving in the third flow path is inserted into the fourth flow path.
The third flow path branches and extends symmetrically left and right from the second flow path when the center housing is viewed from the outside.
The third flow path extends from the second flow path toward the fourth flow path in a direction opposite to gravity.
The third flow path extends longer than the first flow path.
The first sealing part includes a first body part that forms an overall outline and is made of metal or non-metallic material; a first shape maintaining portion formed on the front surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force; It includes a second shape maintaining portion formed on the rear surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force.
A compressor according to a second embodiment of the present invention includes a front housing in which a suction chamber is formed and a driving part for generating a driving force therein; a center housing coupled to face the front housing and having a back pressure chamber formed therein; a turning scroll that receives rotational force from the driving unit on one side facing the center housing; a fixed scroll installed so that the orbiting scroll can rotate and forming a compression chamber together with the orbiting scroll; a rear housing having a discharge chamber configured to accommodate refrigerant discharged from the compression chamber; and a flow path is formed so that a portion of the oil contained in the refrigerant discharged to the discharge chamber is supplied at different flow rates toward the suction chamber and the back pressure chamber, and the flow path extends in a direction opposite to gravity with respect to the center housing. main flow path formed in the section; It includes an auxiliary flow path formed inside the main flow path and having a smaller size than the main flow path.
The auxiliary flow path is formed in a groove shape so that the oil supplied through the main flow path remains, and is formed on either the bottom or side of the main flow path, or on both the bottom and the side.
The auxiliary flow path is formed in the shape of a groove so that the oil supplied through the main flow path remains, and the opposing surface is inclined from the auxiliary flow path to the main flow path so that the opening area toward the main flow path is reduced. is formed
A sealing member for sealing oil moving along the flow path is interposed between the center housing and the orbiting scroll, wherein the sealing member includes: a first sealing portion in close contact with the center housing; One side is in close contact with the first sealing portion, and the other side is in close contact with the orbiting scroll, and includes a second sealing portion made of a different material from the first sealing portion.
The first sealing part includes a first body part that forms an overall outline and is made of metal or non-metallic material; a first shape maintaining portion formed on the front surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force; It includes a second shape maintaining portion formed on the rear surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force.

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Embodiments of the present invention can improve wear resistance by supplying oil necessary for lubrication to the back pressure chamber and the driving part of the compressor, and improve the overall performance of the compressor by simultaneously improving the lubrication performance of the driving part.

Embodiments of the present invention can minimize vibration and noise generation during compressor operation by improving the amount of oil circulation supplied to the driving unit.

Embodiments of the present invention prevent deformation of the first sealing portion and allow tolerances generated between the orbiting scroll and the fixed scroll to be absorbed through the shape maintaining portion, thereby ensuring stable operation even when the compressor is used for a long period of time.

1 is a cross-sectional view showing a compressor according to a first embodiment of the present invention.
Figure 2 is a perspective view showing a center housing and a sealing member according to a first embodiment of the present invention.
Figure 3 is a perspective view showing a center housing according to a first embodiment of the present invention.
Figure 4 is a cross-sectional view showing a flow path according to the first embodiment of the present invention.
Figure 5 is a cross-sectional view showing a compressor according to a second embodiment of the present invention.
Figure 6 is a perspective view showing a center housing and a sealing member according to a second embodiment of the present invention.
7 to 8 are diagrams showing a main flow path and an auxiliary flow path according to a second embodiment of the present invention.

An electric compressor according to an embodiment of the present invention will be described with reference to the drawings. For reference, FIG. 1 is a cross-sectional view showing a compressor according to a first embodiment of the present invention, FIG. 2 is a perspective view showing a center housing and a sealing member according to a first embodiment of the present invention, and FIG. 3 is a compressor according to the first embodiment of the present invention. This is a perspective view showing the center housing according to the first embodiment.

Referring to the attached FIGS. 1 to 3, the compressor 1 according to an embodiment of the present invention transfers oil contained in the refrigerant discharged from the discharge chamber 52 to the suction chamber 12 and the back pressure chamber 22. This relates to a compressor that improves the wear resistance of components that cause friction and wear.

For this purpose, the compressor (1) of the present invention is coupled to a front housing (10) in which a suction chamber (12) is formed and a driving part (2) inside which a driving force is generated, facing the front housing (10). , a center housing 20 with a back pressure chamber 22 formed therein, a turning scroll 30 that receives rotational force from the driving unit 2 on one side facing the center housing 20, and the turning scroll 30 ) is installed to be rotatable, forming a fixed scroll 40 that forms a compression chamber 42 together with the orbiting scroll 30, and a discharge chamber 52 that accommodates the refrigerant discharged from the compression chamber 42. A flow path 100 is provided so that a portion of the oil contained in the refrigerant discharged to the rear housing 50 and the discharge chamber 52 is supplied at different flow rates toward the suction chamber 12 and the back pressure chamber 22. is formed

The compressor 1 has an overall appearance and is composed of a front housing 10, a center housing 20, and a rear housing 50 from one side to the other based on the drawing.

A suction chamber 12 is formed with a predetermined volume inside the front housing 10, and a drive unit 2 is provided in the axial direction at the inner center of the front housing 10.

The driving unit 2 includes a stator 2a located in the inner circumferential direction of the front housing 10, a rotor 2b rotated by interaction with the stator 2a inside the stator 2a, and the It is fastened to the rotor 2b and includes a rotation shaft 2c extending through the center of the front housing 10.

The stator (2a) and the rotor (2b) are accommodated in the suction chamber (12), and the rotation shaft (2c) is moved from the suction chamber (12) via the center housing (20) to the orbiting scroll (30). It extends toward, and the extended end is connected to the orbiting scroll (30).

In this case, when the rotation axis 2c rotates, the orbiting scroll 30 rotates together.

The center housing 20 is coupled to face the front housing 10, and a back pressure chamber 22 is formed therein, and oil for lubrication is supplied to the back pressure chamber 22.

The center housing 20 may communicate with a refrigerant suction pipe (not shown) that guides the refrigerant from the outside of the compressor 1 to the suction chamber 12.

The rear housing 50 is in close contact with one side of the center housing 20 based on the drawing, and is selectively and detachably mounted on the center housing 20. Then, the refrigerant discharged through the orbiting scroll 30 and the fixed scroll 40 is discharged at a predetermined pressure toward the discharge chamber 52 via the back pressure chamber 22.

The rear housing 50 is formed in a structure that partially protrudes outward by a predetermined length because the refrigerant is discharged at a predetermined pressure when the refrigerant is discharged into the discharge chamber 52.

The fixed scroll 40 compresses the refrigerant while the orbiting scroll 30 rotates at a predetermined speed with respect to the fixed scroll 40. The fixed scroll 40 forms a compression chamber 42 together with the orbiting scroll 30.

The flow path 100 according to this embodiment supplies oil at different flow rates to the suction chamber 12 and the back pressure chamber 22 to maintain stable lubrication for components requiring lubrication.

The flow path 100 has a first flow path 110 in communication with the discharge chamber 52, is in communication with the first flow path 110, has one end open in the center housing 20, and has a second end connected to the back pressure. A second flow path 120 opening toward the seal 22, a third flow path 130 communicating with the second flow path 120 and extending upward along the circumferential direction of the center housing 20, It includes a fourth flow path 140, one end of which is connected to the third flow path 130, and the other end of which is open toward the suction chamber 12.

The first passage 110 is opened in the axial direction of the discharge chamber 52 based on the drawing. A first pressure reducing unit 112 is inserted into the first flow path 110 to reduce the pressure of oil moving to the second flow path 120.

The first pressure reducing portion 112 is formed along the axial direction as shown in the drawing, and is formed between the pressure of the discharge chamber 52 and the second flow path 120 corresponding to the outlet of the first flow path 110. It can be formed as a nozzle-type orifice using pressure differences.

The first pressure reducing unit 112 is formed in a cylindrical shape, and a spiral oil transfer groove (G) is formed on the inner peripheral surface. The oil transfer groove (G) provides a transfer path for oil and at the same time reduces the pressure of the refrigerant discharged at high pressure toward the discharge chamber 52 to medium pressure, thereby moving the oil in the direction where the second flow path 120 is formed. To achieve this, the oil is moved to the back pressure chamber (22).

As described above, when oil is supplied through the second flow path 120, the back pressure chamber 22 maintains oil stored at a predetermined height below the rotating shaft 2c. In addition, the back pressure chamber 22 supplies oil to components required for lubrication, thereby reducing wear caused by friction, preventing noise and vibration, and preventing the compressor from stopping due to damage.

In addition, since oil is also supplied to the orbiting scroll 30 and the fixed scroll 40, it is possible to provide stable lubrication and minimize cooling and vibration in areas where sliding occurs due to contact.

Since the refrigerant contains oil, it can stably move from the first flow path 110 toward the second flow path 120 when the pressure is reduced.

In the center housing 20, the second flow path 120 and third to fourth flow paths 130 and 140 are formed on a surface facing the fixed scroll 40. The second to fourth flow paths 120, 130, and 140 are formed in a groove shape as shown in the drawing, but may also be changed to other shapes.

The third flow path 130 has a smaller cross-sectional area than the second flow path 120 and the fourth flow path 140. In this case, the pressure of the oil in the third flow path 130 is reduced compared to the pressure at the position passing through the first flow path 110 and the second flow path 120, but the speed is increased, so that the oil flows into the fourth flow path 140. It moves quickly and stably toward .

If the third flow path 130 has a small cross-sectional area, an orifice effect occurs, so the oil movement speed increases due to the pressure difference.

After passing through the first flow path 110, a portion of the oil is moved to the back pressure chamber 22 via the second flow path 120, and the remaining oil is moved to the fourth flow path through the third flow path 130. It moves to (140).

Since the oil has its own viscosity and friction is inevitably generated while moving along the first to fourth flow passages 110, 120, 130, and 140, the above-described structure is used to ensure stable movement while minimizing resistance. It becomes easier to move around.

Since the third flow path 130 extends in a direction opposite to gravity from the second flow path 120 toward the fourth flow path 140, the oil does not remain only in the inner lower part of the compressor 1 and lubricates according to sliding and friction. Oil is stably supplied to the necessary suction chamber 12 and back pressure chamber 22.

Since the third flow path 130 extends longer than the first flow path 110, stable movement of oil can be achieved through an orifice effect.

Referring to the attached FIG. 2, the third flow path 130 according to the present embodiment extends to the left, for example, when the center housing 20 is viewed from the outside. The extension path of the third flow path 130 extends to the location where the driving unit 2 is located based on the drawing, considering the layout in close contact with the center housing 20 and the rear housing 50 when assembled.

As an example, the third flow path 130 extends in a direction opposite to gravity, and can supply oil to the drive unit 2 to provide stable lubrication to various bearings or locations where sliding occurs.

In this embodiment, a sealing member 200 is interposed between the center housing 20 and the orbiting scroll 30 to seal the oil moving from the first flow path 110 to the fourth flow path 140. .

The sealing member 200 has a first sealing part 210 in close contact with the center housing 20, one side is in close contact with the first sealing part 210, and the other side is in close contact with the orbiting scroll 30. It includes a second sealing part 220 made of a different material from the first sealing part 210.

The first sealing part 210 and the second sealing part 220 are made of different materials, and are not limited to a specific material.

The first sealing part 210 forms an overall outline and includes a first body part 214 made of metal or non-metallic material, is formed to a predetermined thickness on the front surface of the first body part 214, and has a predetermined elastic restoring force. It includes a first shape maintaining part 216 that is maintained, and a second shape maintaining part 218 that is formed at a predetermined thickness on the rear side of the first body part 214 and maintains a predetermined elastic restoring force.

The first body portion 214 is formed of a metallic material such as steel or a non-metallic material in order to stably maintain the overall shape of the first sealing portion 210, and is not limited to a specific material.

If the first body portion 214 is made of a metal material, deformation due to twisting can be minimized and it can be used stably even for long-term use.

For example, the first and second shape maintaining parts 216 and 218 are made of rubber, but they may also be made of other materials that maintain elastic restoring force.

The first and second shape maintaining portions 216 and 218 can absorb axial tolerances occurring between the orbiting scroll 30 and the fixed scroll 40 with their own elastic restoring force, thereby absorbing vibration in the axial direction during operation. and stable operation can be achieved by absorbing tolerances.

The first and second sealing parts 210 and 220 protrude in the outer circumferential direction and are formed with protruding pieces 211 and 222 spaced apart at a predetermined interval. In the protruding pieces 211 and 222, the mounting holes 211a and 222a are not formed in all of the protruding pieces 211 and 222a, but are formed in some of the protruding pieces 211 and 222a. For example, in the drawing shown in FIG. 2, mounting holes 211a and 222a are formed at 2 o'clock, 6 o'clock, and 9 o'clock clockwise.

The protruding pieces (211, 222a) are positioned at the positions where the mounting holes (211a, 222a) are formed, and a positioning pin (not shown) is inserted so that the worker is in close contact with the center housing (20) when assembling the compressor (1). ,2 Enables installation of the sealing portions 210 and 220 in the correct position.

A first pin groove 21 into which the positioning pin is coupled is formed in the center housing 20.

In the case where the mounting holes 211a and 222a are not formed in the protruding pieces 211 and 222a, the correct direction can be distinguished by guiding the position and preventing rotation or separation when the worker assembles.

Center holes (210a, 220a) into which the rotation axis (2c) or eccentric bushing are inserted are formed at the exact center of the first and second sealing parts (210, 220), and the radial outer circumference of the center holes (210a, 220a) A plurality of penetrating side holes 210b and 220b are formed at predetermined intervals in the direction.

The side holes (210b, 220b) are holes where pins (not shown) are coupled in a pin-and-ring structure that prevents rotation, and are located in the center housing (20) where the first and second sealing parts (210, 220) are installed. The pin is coupled to the second pin groove 21 formed on the opposing surface.

The second sealing part 220 according to this embodiment is formed to be relatively thicker than the first sealing part 210 because it contacts the orbiting scroll 30 while rotating relative to it. In this case, the rigidity of the second sealing portion 220 is maintained constant and deformation is minimized even when continuous contact is maintained.

When the first sealing part 210 is in close contact with the first to fourth flow passages 110, 120, 130, and 140, it can prevent oil leakage and maintain stable operation of the compressor 1.

The second sealing portion 220 is made of steel or a material with wear resistance similar to steel to prevent wear due to continuous contact and friction with the orbiting scroll 30, so even when it is in close contact with the orbiting scroll 30, the second sealing portion 220 is made of steel or a material having wear resistance similar to steel. 1 It does not affect the stable sealing of the sealing part 210.

For example, the hardness of the second sealing part 220 that slides while being in contact with the orbiting scroll 30 may be relatively greater than that of the first sealing part 210 that is in contact with the center housing 20.

Therefore, even when the compressor 1 is operated for a long period of time, oil leakage does not occur due to oil movement, and the oil supply to the suction chamber 12 and the back pressure chamber 22 is maintained stably.

The first sealing portion 210 according to this embodiment is formed so that the portion corresponding to the edge of the outer diameter is located radially outside the position of the third passage 130, so that problems due to leakage do not occur. It can be used stably.

The second sealing part 220 according to this embodiment has an outer diameter border that is larger than or equal to the radius of the orbiting scroll 30, so it can be used stably without problems due to leakage.

Referring to the attached FIG. 3, the third flow path 130 according to the present embodiment branches and extends symmetrically from the second flow path 120 when the center housing 20 is viewed from the outside.

Unlike the above-described embodiment, the third flow path 130 branches off and extends to the left and right from the second flow path 120 formed in the center housing 20 toward the driving unit 2, respectively.

When the third flow path 130 is extended in this way, the oil moves more stably because a plurality of paths are formed along which the oil moves toward the suction chamber 12 or the drive unit 2 along a movement path extending to the right or left. .

For example, the third flow path 130 allows oil to stably move along the other extended movement path even if one of the movement paths extending to the left or right of the center housing 20 is blocked or closed. This improves movement stability.

Therefore, the third flow path 130 can stably supply oil to the suction chamber 12 and the back pressure chamber 22, so that a certain amount of oil always remains and the oil circulation rate is improved.

Referring to the attached FIG. 4, the first sealing part 210 is formed with an insertion protrusion 212 inserted into the opened inside of the second to fourth flow paths 120, 130, and 140.

The first sealing portion 210 maintains a state in which the counter surface facing the second to fourth flow passages 120, 130, and 140 is closed face-to-face, and the insertion protrusion 212 has a predetermined shape on the inner surface. Since it is inserted lengthwise, external oil leakage does not occur.

The insertion protrusion 212 is inserted into the second to fourth passages 120, 130, and 140 with a predetermined thickness (t) and length (L), and is not limited to the thickness and length shown in the drawing.

In this embodiment, the first flow path 110 and the fourth flow path 140 are not arranged in series, so the oil can be moved to the fourth flow path 140 along the third flow path 130 in a direction opposite to the direction of gravity. .

The fourth flow path 140 is open toward the suction chamber 12, so that when oil is supplied to the suction chamber 12, a stable oil film can be formed on the components required for lubrication.

A second pressure reducing unit 142 is inserted into the fourth flow path 140 to reduce the pressure of oil moving in the third flow path 130. The second pressure reducing unit 142 is formed in a cylindrical shape, and a spiral oil transfer groove (G) is formed on its inner peripheral surface. The oil transfer groove (G) provides a transfer path for oil and at the same time reduces the pressure of the refrigerant and guides the movement of the oil into the suction chamber (12).

A compressor according to a second embodiment of the present invention will be described with reference to the drawings.

Referring to the attached FIGS. 5 and 6, this embodiment, unlike the first embodiment described above, can achieve stable lubrication of the compressor by improving the stability of oil movement through the auxiliary passage and resolving problems caused by oil shortage. .

For this purpose, this embodiment includes a front housing 10 in which a suction chamber 12 is formed and a driving part 2 inside which a driving force is generated, which is coupled to face the front housing 10 and has a back pressure chamber inside the front housing 10. A center housing 20 formed with (22), a turning scroll 30 that receives rotational force from the driving unit 2 on one side facing the center housing 20, and the turning scroll 30 is rotatable. A rear housing (50) having a fixed scroll (40) installed to form a compression chamber (42) together with the orbiting scroll (30), and a discharge chamber (52) in which refrigerant discharged from the compression chamber (42) is accommodated. And a flow path 1000 is formed so that a portion of the oil contained in the refrigerant discharged to the discharge chamber 52 is supplied at different flow rates toward the suction chamber 12 and the back pressure chamber 22.

The flow path 1000 includes a main flow path 1300 formed in a section extending in a direction opposite to gravity based on the center housing 20, and a size smaller than the main flow path 1300 inside the main flow path 1300. It includes an auxiliary flow path 1350 formed by .

The flow path 1000 communicates with the first flow path 1100 in communication with the discharge chamber 52, has one end open in the center housing 20, and has a second end open to the back pressure. A second flow path 1200 opened toward the seal 22, a main flow path 1300 that communicates with the second flow path 1200 and extends upward along the circumferential direction of the center housing 20, and one end thereof It is connected and includes a fourth flow path 1400 whose other end is open toward the suction chamber 12.

Since the first and second flow paths 1100 and 1200 and the fourth flow path 1400 are similar to the first and second flow paths 110 and 120 described in the above-described first embodiment, detailed description will be omitted and the auxiliary flow path 1350 ) will be explained mainly.

A sealing member 200 for sealing oil moving along the flow path 1000 is interposed between the center housing 20 and the orbiting scroll 30. The sealing member 200 has a first sealing part 210 that is in close contact with the center housing 20 and is made of an elastic material, one side is in close contact with the first sealing part 210, and the other side is in close contact with the orbiting scroll 30. ) and includes a second sealing part 220 that is in close contact with the first sealing part 210 and made of a different material.

The first sealing part 210 and the second sealing part 220 are made of different materials, and are not limited to a specific material.

The first sealing part 210 forms an overall outline and includes a first body part 214a made of metal or non-metallic material, is formed to a predetermined thickness on the front surface of the first body part 214a, and has a predetermined elastic restoring force. It includes a first shape maintaining part 216a that is maintained, and a second shape maintaining part 218a that is formed at a predetermined thickness on the rear surface of the first body part 214a and maintains a predetermined elastic restoring force.

The first body portion 214a is formed of a metallic material such as steel or a non-metallic material in order to stably maintain the overall shape of the first sealing portion 210, and is not limited to a specific material.

If the first body portion 214a is made of a metal material, deformation due to twisting can be minimized and it can be used stably even for long-term use.

For example, the first and second shape maintaining parts 216a and 218a are made of rubber, but they may also be made of other materials that maintain elastic restoring force.

The first and second shape maintaining portions 216a and 218a can absorb axial tolerances occurring between the orbiting scroll 30 and the fixed scroll 40 with their own elastic restoring force, thereby absorbing vibration in the axial direction during operation. and stable operation can be achieved by absorbing tolerances.

The first and second sealing parts 210 and 220 protrude in the outer circumferential direction and are formed with protruding pieces 211 and 222 spaced apart at a predetermined interval. In the protruding pieces 211 and 222, the mounting holes 211a and 222a are not formed in all of the protruding pieces 211 and 222a, but are formed in some of the protruding pieces 211 and 222a. For example, in the drawing shown in FIG. 6, mounting holes 211a and 222a are formed at 2 o'clock, 6 o'clock, and 9 o'clock clockwise.

The protruding pieces (211, 222a) are positioned at the positions where the mounting holes (211a, 222a) are formed, and a positioning pin (not shown) is inserted so that the worker is in close contact with the center housing (20) when assembling the compressor (1). ,2 Enables installation of the sealing portions 210 and 220 in the correct position.

A first pin groove 21 into which the positioning pin is coupled is formed in the center housing 20.

In the case where the mounting holes 211a and 222a are not formed in the protruding pieces 211 and 222a, the correct direction can be distinguished by guiding the position and preventing rotation or separation when the worker assembles.

Center holes (210a, 220a) into which the rotation axis (2c) or eccentric bushing are inserted are formed at the exact center of the first and second sealing parts (210, 220), and the radial outer circumference of the center holes (210a, 220a) A plurality of penetrating side holes 210b and 220b are formed at predetermined intervals in the direction.

The side holes (210b, 220b) are holes where pins (not shown) are coupled in a pin-and-ring structure that prevents rotation, and are located in the center housing (20) where the first and second sealing parts (210, 220) are installed. The pin is coupled to the second pin groove 21 formed on the opposing surface.

The second sealing part 220 according to this embodiment is formed to be relatively thicker than the first sealing part 210 because it contacts the orbiting scroll 30 while rotating relative to it. In this case, the rigidity of the second sealing portion 220 is maintained constant and deformation is minimized even when continuous contact is maintained.

The first sealing part 210 can prevent oil leakage when it is in close contact with the first and second flow paths 1100 and 1200, the auxiliary flow path 1350, and the fourth flow path 1400, thereby ensuring a stable operation of the compressor 1. operation can be maintained.

The second sealing portion 220 is made of steel or a material with wear resistance similar to steel to prevent wear due to continuous contact and friction with the orbiting scroll 30, so even when it is in close contact with the orbiting scroll 30, the second sealing portion 220 is made of steel or a material having wear resistance similar to steel. 1 It does not affect the stable sealing of the sealing part 210.

For example, the hardness of the second sealing part 220 that slides while being in contact with the orbiting scroll 30 may be relatively greater than that of the first sealing part 210 that is in contact with the center housing 20.

The first sealing portion 210 according to this embodiment is formed so that the portion corresponding to the border of the outer diameter is located radially outside the position of the main passage 1300, so that problems due to leakage do not occur and it is stable. It can be used as

The second sealing part 220 according to this embodiment has an outer diameter border that is larger than or equal to the radius of the orbiting scroll 30, so it can be used stably without problems due to leakage.

Referring to the attached FIG. 7, the auxiliary flow path 1350 is formed in a groove shape so that the oil supplied through the main flow path 1300 remains, and is formed on the bottom surface 1310 or the side surface 1320 of the main flow path 1300. ) or one formed on both the bottom surface 1310 and the side surface 1320. For reference, this embodiment shows that the auxiliary flow path 1350 is formed on the bottom surface 1310.

The auxiliary flow path 1350 is formed in the suction chamber 12 through the second flow path 1200 through a pressure difference after the oil contained in the refrigerant discharged to the discharge chamber 52 is supplied to the first flow path 1100. ) is supplied.

Additionally, the oil is supplied to the fourth flow path 1400 along the main flow path 1300 and then supplied to the back pressure chamber 22.

When the oil is supplied to the suction chamber 12 and the back pressure chamber 22, the oil is supplied to the components required for lubrication, thereby reducing wear caused by friction, preventing noise and vibration, and stopping the compressor due to damage. The condition can be prevented.

The auxiliary flow path 1350 is formed in the shape of a groove so that the oil supplied through the main flow path 1300 remains. When oil is supplied to the auxiliary flow path 1350 through the main flow path 1300, a certain amount of oil is stored and supplied simultaneously.

For example, when the auxiliary flow path 1350 is formed together with the main flow path 1300 rather than the configuration in which only the main flow path 1300 is formed, a certain amount of oil always remains inside the auxiliary flow path 1350. In this case, oil is continuously supplied to the suction chamber 12 and the back pressure chamber 22, thereby maintaining stable lubrication for components that are in constant contact and friction.

Since the remaining oil is moved to the auxiliary passage 1350 through the pressure difference between the discharge chamber 52, the suction chamber 12, and the back pressure chamber 22, the phenomenon of oil being depleted or not supplied occurs.

The auxiliary flow path 1350 can be changed to other forms other than those shown in the drawing, and is not particularly limited.

The auxiliary flow path 1350 is formed with an inclined portion 1352 whose opposing surface is inclined from the auxiliary flow path 1350 to the main flow path 1300 so that the open area toward the main flow path 1300 is reduced. .

The inclined portion 1352 serves to prevent the oil stored inside the auxiliary flow path 1350 from moving into the open area of the main flow path 1300, and prevents the oil moving through the auxiliary flow path 1350 from moving. It is formed to further improve movement stability through pressure differences.

That is, the inclined portion 1352 reduces the internal space of the auxiliary flow path 1350 so that oil remains in most of the open areas of the auxiliary flow path 1350, so that a certain amount of oil is always maintained regardless of whether oil remains in the main flow path 1300. Oil may remain.

In this case, oil is supplied to the above-mentioned suction chamber 12 and back pressure chamber 22, but the amount of oil supplied varies depending on the pressure, so the amount of oil supplied changes depending on the number of revolutions per minute or the load state of the compressor 1.

Referring to the attached FIG. 8, this embodiment shows the state of the oil in the main passage 1300 under the condition that the compressor 1 is stopped for a certain period of time, and the oil remaining in the main passage 1300 is higher than when it is normally operated. This may be insufficient. It is advantageous for oil to remain in the main passage 1300 for stable oil supply to the suction chamber 12 and the back pressure chamber 22, but when the compressor 1 is not used, such as in winter, the remaining oil It is minimized.

In this embodiment, in order to solve this problem, a minimum amount of oil remains inside the auxiliary passage 1350, thereby solving the problem of lubrication of the sliding part due to lack of oil.

Since excess oil required for lubrication remains in the auxiliary passage 1350, when the compressor 1 that is not in use in an off state is restarted, oil for minimum lubrication is supplied through the auxiliary passage 1350, thereby improving lubrication performance. can be promoted.

In addition, the oil supply to the suction chamber 12 and the back pressure chamber 22 is maintained stably due to the oil remaining in the auxiliary passage 1350, so that stable lubrication of the sliding surface is achieved even when the operation is suddenly started after being stopped for a long period of time. .

Above, an embodiment of the present invention has been described, but those skilled in the art can add, change, delete or add components without departing from the spirit of the present invention as set forth in the patent claims. The present invention may be modified and changed in various ways, and this will also be included within the scope of rights of the present invention.

1: Compressor
10: front housing
20: Center housing
30: orbiting scroll
40: fixed scroll
50: rear housing
100, 1000: Euro
110: 1st Euro
120: 2nd Euro
130: 3rd euro
140: 4th euro
200: Sealing part
1300: Main Euro
1350: Secondary Euro

Claims (16)

A front housing in which a suction chamber is formed and a driving part that generates driving force is provided therein;
a center housing coupled to face the front housing and having a back pressure chamber formed therein;
a turning scroll that receives rotational force from the driving unit on one side facing the center housing;
a fixed scroll installed so that the orbiting scroll can rotate and forming a compression chamber together with the orbiting scroll;
a rear housing having a discharge chamber configured to accommodate refrigerant discharged from the compression chamber; and
A flow path is formed so that a portion of the oil contained in the refrigerant discharged to the discharge chamber is supplied at different flow rates toward the suction chamber and the back pressure chamber,
The flow path includes a first flow path in communication with the discharge chamber, a second flow path in communication with the first flow path, one end of which is open in the center housing, and the other end of which is open toward the back pressure chamber, and the second flow path, A third flow path is in communication and extends upward along the circumferential direction of the center housing, and a fourth flow path has one end connected to the third flow path and the other end open toward the suction chamber,
The second flow path and the fourth flow path are formed on opposing surfaces of the center housing facing the fixed scroll. delete According to claim 1,
The compressor wherein the third flow path has a smaller cross-sectional area than the second flow path and the fourth flow path. According to claim 1,
A sealing member for sealing oil moving along the fourth flow path from the first flow path is interposed between the center housing and the orbiting scroll,
The sealing member includes a first sealing portion in close contact with the center housing;
A compressor including a second sealing portion that has one side in close contact with the first sealing portion and the other side in close contact with the orbiting scroll and is made of a different material from the first sealing portion. According to clause 4,
The first sealing part is a compressor in which an insertion protrusion is inserted into the opening of the second to fourth flow paths. According to claim 1,
A compressor in which a first pressure reducing unit is inserted into the first flow path to reduce the pressure of oil moving to the second flow path. According to claim 1,
A compressor in which a second pressure reducing unit is inserted into the fourth flow path to reduce the pressure of oil moving in the third flow path. According to claim 1,
The third flow path is symmetrically branched and extended from the second flow path when the center housing is viewed from the outside. According to claim 1,
The third flow path is a compressor extending in a direction opposite to gravity from the second flow path toward the fourth flow path. According to claim 1,
The third flow path is a compressor extending longer than the first flow path. According to clause 4,
The first sealing part includes a first body part that forms an overall outline and is made of metal or non-metallic material;
a first shape maintaining portion formed on the front surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force;
A compressor including a second shape maintaining portion formed on the rear surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force. A front housing in which a suction chamber is formed and a driving part that generates driving force is provided therein;
a center housing coupled to face the front housing and having a back pressure chamber formed therein;
a turning scroll that receives rotational force from the driving unit on one side facing the center housing;
a fixed scroll installed so that the orbiting scroll can rotate and forming a compression chamber together with the orbiting scroll;
a rear housing having a discharge chamber configured to accommodate refrigerant discharged from the compression chamber; and
A flow path is formed so that a portion of the oil contained in the refrigerant discharged to the discharge chamber is supplied at different flow rates toward the suction chamber and the back pressure chamber,
The flow path includes a main flow path formed in a section extending in a direction opposite to gravity with respect to the center housing;
A compressor including an auxiliary flow path formed inside the main flow path and having a smaller size than the main flow path. According to claim 12,
The auxiliary flow path is formed in the shape of a groove so that the oil supplied through the main flow path remains,
A compressor consisting of one of the bottom or sides of the main flow passage, or one formed on both the bottom and the sides. According to claim 12,
The auxiliary flow path is formed in the shape of a groove so that the oil supplied through the main flow path remains,
A compressor in which an inclined portion is formed where the opposing surface is inclined from the auxiliary flow path to the main flow path so that the opening area toward the main flow path is reduced. According to claim 12,
A sealing member for sealing oil moving along the flow path is interposed between the center housing and the orbiting scroll,
The sealing member includes a first sealing portion in close contact with the center housing;
A compressor including a second sealing portion that has one side in close contact with the first sealing portion and the other side in close contact with the orbiting scroll and is made of a different material from the first sealing portion. According to claim 15,
The first sealing part includes a first body part that forms an overall outline and is made of metal or non-metallic material;
a first shape maintaining portion formed on the front surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force;
A compressor including a second shape maintaining portion formed on the rear surface of the first body portion to a predetermined thickness and maintaining a predetermined elastic restoring force.