KR20230121226A - Scroll Compressor - Google Patents

Abstract

The present invention, a rotating shaft; an orbiting scroll installed on the rotating shaft to be able to rotate and having a ring receiving groove on one surface thereof; a fixed scroll engaged with the orbiting scroll to form a compression chamber between the orbiting scroll and the fixed scroll; A front housing installed on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween and having an orbiting contact surface for supporting the orbiting scroll so as to orbitally rotate, an anti-rotation ring coupled to the ring receiving groove, At least a part of the orbiting contact surface is provided with an anti-rotation pin disposed so as to come into contact with an inner circumference of the orbiting scroll to guide orbital rotation of the orbiting scroll, and in the front housing, the orbiting contact surface is disposed on one surface of the orbiting scroll. A direct contact scroll compressor is provided.

Description

Scroll Compressor

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having a structure capable of improving reliability between an orbiting scroll and a front housing.

In general, a compressor is a device for compressing a fluid such as a refrigerant gas, and may be classified into a rotary compressor, a reciprocating compressor, a scroll compressor, and the like according to a method of compressing the fluid.

The scroll compressor is a high-efficiency, low-noise compressor widely applied in the field of air conditioners. Two scrolls having a fixed wrap and an orbiting wrap form a plurality of compression chambers in pairs between the fixed wrap and the orbiting wrap of each scroll while performing relative orbital movements. As the compression chamber continuously moves toward the center and decreases in volume, the refrigerant is continuously sucked, compressed, and discharged.

On the other hand, a heat pump refers to absorbing heat from low-temperature heat and transferring the heat to high-temperature heat, and using low-temperature heat is usually called a refrigerator, while using high-temperature heat is called a heat pump. It is commonly referred to as a heat pump.

There are various types of heat pumps, such as compression type, chemical formula, absorption type, and adsorption type, depending on the method of absorbing and dissipating heat. method, and GHP (Gas Heat Pump) method using a gas engine to drive the compressor.

The compressor applied to the GHP is mechanical (belt driven) and has a structure very similar to that of the existing air conditioning compressor for automobiles.

In addition, an anti-rotation structure is applied to the compressor, and there are two types of anti-rotation structures: a ball coupling structure and a pin and ring structure.

Among these two anti-rotation structures, the pin-and-ring structure is mainly used to reduce material costs.

The pin-and-ring structure may include a pin provided on the front housing, a thrust plate, and a ring installed on the rear side of the orbiting scroll.

The ring of the pin-and-ring structure is restrained in the radial direction by the pin, preventing rotation and performing a turning motion like a turning scroll.

At this time, the diameter of the pin has a correlation with the inner diameter of the ring, and 2* turning radius (ε) + diameter of the pin (d _pin ) must be the inner diameter (r _i ) of the ring, and the anti-rotation function can be performed only when this is satisfied. will have

In addition, the thrust plate is provided with several holes into which pins can enter, is seated in the front housing, and performs a frictional motion with the rear surface of the orbiting scroll.

In the pin-and-ring structure, it is required to examine the pin-and-ring structure for reducing material cost or the number of parts, simplifying the structure, and improving assemblability.

In particular, in the case of the conventional pin-and-ring structure, the front housing and the orbiting scroll are made of aluminum because weight reduction is very important due to the characteristics of the compressor for air conditioning of automobiles.

In order to avoid direct friction between the front housing and the orbiting scroll, which are made of the same material, a thrust plate made of a different material (iron or other type) exists between the two parts.

However, in the conventional compressor, there were two problems.

The first problem is that the inner diameter of the hole of the thrust plate exerts an impact on the pin because it is usually assembled in a state where the inner diameter of the hole of the thrust plate is larger than the diameter of the pin between the relative movement between the front housing and the orbiting scroll.

The second problem is that since the depth at which the pins are driven by the thickness of the thrust plate is reduced, the distance to the force generated on the pins increases, resulting in a large moment load.

As a result, various types of reliability problems such as breakage of pins or rings and seizure between the orbiting scroll and the thrust plate occur.

In addition, in the case of a structure in which an oil groove is formed in the orbiting head plate of the existing orbiting scroll, there is a problem of interference with the ring groove in which the anti-rotation ring is installed in the orbiting head.

Therefore, the impact applied between the front housing and the orbiting scroll is mitigated, and the moment load applied to the pin is reduced to improve reliability between the front housing and the orbiting scroll, and the interference problem between the ring groove and the oil groove can be reduced. The development of a scroll compressor is required.

The present invention has been made to solve the above problems, and a first object of the present invention is to mitigate the impact applied between the front housing and the orbiting scroll, and reduce the moment load applied to the pin so that the front housing and the orbit It is to provide a scroll compressor having a structure that improves reliability between scrolls.

Further, a second object of the present invention is to provide a scroll compressor having a structure that enables reduction in the number of parts, simplification of the structure accordingly, reduction in material cost, and improvement in assemblability.

In addition, a third object of the present invention is to provide a scroll compressor capable of alleviating the problem of interference with the ring groove in which the anti-rotation ring is installed in the orbiting head plate due to the formation of the oil groove in the orbiting head plate of the orbiting scroll. is to do

In addition, a fourth object of the present invention is to provide a scroll compressor in which oil can flow in the radial and circumferential directions on the orbiting contact surface of the front housing, thereby improving reliability between the front housing and the orbiting scroll.

In order to solve the above problems, the scroll compressor of the present invention, the rotating shaft; an orbiting scroll installed on the rotating shaft to be able to rotate and having a ring receiving groove on one surface thereof; a fixed scroll engaged with the orbiting scroll to form a compression chamber between the orbiting scroll and the fixed scroll; A front housing installed on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween and having an orbiting contact surface for supporting the orbiting scroll so as to orbitally rotate, an anti-rotation ring coupled to the ring receiving groove, At least a part of the orbiting contact surface is provided with an anti-rotation pin disposed so as to come into contact with an inner circumference of the orbiting scroll to guide orbital rotation of the orbiting scroll, and in the front housing, the orbiting contact surface is disposed on one surface of the orbiting scroll. come in direct contact

By removing the thrust plate and having a structure in which the front housing and the orbiting scroll perform relative motion by direct friction, the impact applied between the front housing and the orbiting scroll is relieved and the moment load applied to the pin is reduced, thereby reducing the front housing and the orbiting scroll. Reliability can be improved between scrolls.

In addition, in the present invention, since the front housing directly rubs against one surface of the orbiting scroll so that the pin can be deeply embedded in the front housing as much as the thickness of the existing thrust plate, the distance from the position where the force is generated is reduced, thereby reducing the moment load. do.

A concave oil supply groove may be formed on the pivot contact surface, and the oil supply groove may include a plurality of first oil supply grooves formed in a radial direction and spaced apart from each other in a circumferential direction.

As the oil supply groove is formed on the turning contact surface of the front housing, it is possible to prevent an interference problem between the ring groove where the anti-rotation ring is installed and the oil groove, which occurs in a structure in which an oil groove is formed in a conventional orbiting scroll.

The oil supply groove may further include a second oil supply groove provided to cross the first oil supply groove and formed in a circumferential direction.

Due to this, oil can flow in the radial and circumferential directions on the orbiting contact surface of the front housing, so that reliability between the front housing and the orbiting scroll can be improved.

The second oil supply groove may be formed in plurality, and a cross end portion communicating with the first oil supply groove may be provided at an end portion of each of the second oil supply grooves in a circumferential direction.

The front housing and the orbiting scroll may be formed of different materials.

Preferably, the front housing may be formed of cast iron, and the orbiting scroll may be formed of aluminum.

Due to this, a structure capable of direct friction between the orbiting scroll and the front housing is formed, and since a separate thrust plate is not required between the two, the reliability of the pin-and-ring structure can be improved.

The front housing has, at an end, a support wall portion having the pivoting contact surface and extending in an extension direction of the rotation shaft, and the first oil supply groove includes an inner end groove penetrating an inner circumference of the support wall portion, and the support wall portion. An outer end groove penetrating the outer circumference of the wall portion may be provided.

The second oil supply groove may be provided at the center between the inner end groove and the outer end groove in the radial direction.

The front housing has, at an end, a support wall portion having the pivoting contact surface and extending in an extension direction of the rotation shaft, and the first oil supply groove has both ends spaced apart from each other on the inner circumference and the outer circumference of the support wall portion. It may be formed so as not to penetrate the inner and outer circumferences of the support wall portion.

A concave oil supply groove may be formed on the pivoting contact surface, and a second oil supply groove formed in a circumferential direction may be included.

The oil supply groove may further include a third oil supply groove communicating with the second oil supply groove to guide oil to the second oil supply groove and radially communicating with the second oil supply groove.

The scroll compressor of the present invention eliminates the thrust plate, and directs friction between the front housing and the orbiting scroll to cause relative motion, thereby alleviating the impact applied between the front housing and the orbiting scroll and reducing the moment load applied to the pins, thereby reducing the front housing Reliability can be improved between the and the orbiting scroll.

In the present invention, since the front housing directly rubs against the second surface and the pin can be deeply driven into the front housing by the thickness of the existing thrust plate, the distance from the position where the force is generated is reduced, thereby reducing the moment load.

In particular, since the orbiting scroll may be formed of aluminum, and the front housing is formed of a casting material and is formed of a different material, the orbiting scroll is formed of a different material from the front housing, so that the orbiting scroll and the front housing can be directly rubbed. The reliability of the pin-and-ring structure can be improved by forming a structure and eliminating the need for a separate thrust plate between the two.

In the present invention, as a result of structural analysis, it can be confirmed that the stress at the root of the pin is improved by 11.4% compared to the prior art.

That is, according to the present invention, the insertion depth of the anti-rotation pin is increased, and bending of the pin can be suppressed.

In addition, the present invention, looking at the structural analysis results, the maximum stress applied to the pin has an improvement effect that the stress is reduced by 11.4% in the present invention compared to the prior art.

In addition, according to the present invention, as the number of parts is reduced and, in particular, the thrust plate is removed, it is possible to simplify the structure accordingly, to reduce material and manufacturing costs, and to improve assemblability.

In addition, the present invention, as the oil supply groove is formed on the turning contact surface of the front housing, the interference problem between the ring groove and the oil groove in which the anti-rotation ring is installed, which occurred in the structure in which the oil groove is formed in the conventional orbiting scroll, is solved. It can be prevented.

In addition, in the present invention, the second oil supply groove can be formed in the circumferential direction between the inner end groove and the outer end groove of the first oil supply groove, so that oil can flow in the radial and circumferential directions on the pivoting contact surface of the front housing. Thus, reliability between the front housing and the orbiting scroll can be improved.

1 is a plan view showing a scroll compressor of the present invention;
Figure 2 is a cross-sectional view showing the inside of the scroll compressor of the present invention.
Figure 3 is an exploded perspective view showing the disassembled scroll compressor of the present invention.
4 is a perspective view illustrating an example in which a front housing and an orbiting scroll are combined;
5 is an exploded perspective view showing a front housing and an orbiting scroll disassembled;
6 is an exploded perspective view of FIG. 5 viewed from below;
7 is a perspective view of a front housing;
8 is a plan view of the front housing;
9 is a perspective view schematically showing a pin among pins and rings in the present invention;
10 is a conceptual diagram illustrating a structural analysis performed on a pin installed in a front housing of a conventional structure.
11 is a conceptual diagram illustrating structural analysis of a pin installed in a front housing in the present invention.

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

In this specification, the same or similar reference numerals are given to the same or similar components even in different embodiments, and overlapping descriptions thereof will be omitted.

In addition, a structure applied to one embodiment may be equally applied to another embodiment as long as there is no structural or functional contradiction between different embodiments.

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

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

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

The scroll compressor 100 of the present invention includes a rotating shaft 20, an orbiting scroll 30, a fixed scroll 40, and a front housing 12.

The orbiting scroll 30 is installed so as to be able to orbitally rotate on the rotary shaft 20, and is provided with a ring receiving groove 31a on one surface.

The fixed scroll 40 is engaged with the orbiting scroll 30 to form a compression chamber V between the orbiting scroll 30 and the fixed scroll 40 .

The front housing 12 is installed on the opposite side of the fixed scroll 40 with the orbiting scroll 30 interposed therebetween. In addition, the front housing 12 has a turning contact surface 12a-1 that comes into contact with one surface where the ring receiving groove 31a of the turning scroll 30 is provided.

The orbiting contact surface 12a-1 of the front housing 12 is a surface that supports the orbiting scroll 30 so as to be able to orbitally rotate.

When the orbiting scroll 30 and the front housing 12 are made of the same material, a thrust plate (not shown) is coupled between the front housing 12 and the orbiting scroll 30 to rotate the front housing 12 and The load and friction between the scrolls 30 in the axial direction can be reduced.

However, in the present invention, the orbiting scroll 30 and the front housing 12 are formed of different materials, and therefore, a thrust plate is not provided between the orbiting scroll 30 and the front housing 12 .

The scroll compressor 100 of the present invention may include an anti-rotation member 70 to which a pin-and-ring structure is applied to prevent the orbiting scroll 30 from rotating.

For example, an anti-rotation ring 72 is coupled to the ring receiving groove 31a provided on one surface of the orbiting scroll 30, and an anti-rotation pin 71 is coupled to the orbiting contact surface 12a-1 of the front housing 12. ) is installed. At least a part of the anti-rotation pin 71 is disposed to come into contact with the inner circumference of the anti-rotation ring 72 to guide the turning rotation of the orbiting scroll 30 .

In addition, an oil supply groove 12c is formed on the pivot contact surface 12a-1. The oil supply groove 12c is formed concavely in the pivoting contact surface 12a-1, and includes the first oil supply groove 12c-1.

The first oil supply groove 12c-1 is formed radially in the turning contact surface 12a-1. In addition, a plurality of first oil supply grooves 12c-1 are formed, and the plurality of first oil supply grooves 12c-1 are spaced apart from each other in the circumferential direction.

Detailed structures of the front housing 12 and the fixed scroll 40 will be described later, and the orbiting scroll 30 will be described once.

The orbiting scroll 30 is disposed so as to be orbitally rotatable with respect to the fixed scroll 40 .

The orbiting scroll 30 is made to form a compression chamber (V) together with the fixed scroll (40).

The orbiting scroll 30 is connected to an orbiting wrap 32 engaged with the fixed wrap 42 of the fixed scroll 40 to form a compression chamber V at one end of the orbiting wrap 32 and has a predetermined width. The orbiting mirror plate portion 31 formed of , and the shaft coupling portion 33 formed in the opposite direction of the orbiting wrap 32 in the orbiting mirror plate portion 31 may be provided.

The orbiting scroll 30 is disposed at a position facing the fixed scroll 40 . The orbiting scroll 30 is coupled to the eccentric bush 25 of the rotary shaft 20 . Accordingly, the orbiting scroll 30 is coupled to the rotary shaft 20 so as to be capable of orbiting rotation.

The orbiting scroll 30 receiving rotational force through the eccentric bush 25 is rotated by the anti-rotation member 70 .

For example, the orbiting scroll 30 may be formed of aluminum or an alloy containing aluminum to be advantageous for high-speed orbital rotational motion.

In the present invention, since the orbiting scroll 30 is formed of a different material from the front housing 12, the orbiting scroll 30 and the front housing 12 can directly rub against each other, and the orbiting scroll 30 and the front housing (12) It becomes a structure that does not require a separate thrust plate between them.

Accordingly, it is possible to prevent an impact from being applied due to contact between the inner diameter of the hole provided in the existing thrust plate and the anti-rotation pin 71 .

In addition, since the anti-rotation pin 71 can be driven deeper by the thickness of the thrust plate, the distance from the position where the force is generated is reduced, thereby reducing the moment load.

In this way, the orbiting scroll 30 is formed of a different material from the front housing 12 to form a structure capable of direct friction between the orbiting scroll 30 and the front housing 12, and separate thrust between the two. The reliability of the pin-and-ring structure can be improved because the plate is not required.

The orbiting scroll 30 includes an orbiting head plate part 31, an orbiting wrap 32, an axis coupling part 33, and a ring receiving groove 31a.

The turning head plate part 31 is formed in a plate shape corresponding to the fixed head plate part 41 to be described later. If the turning mirror plate part 31 has a cross section corresponding to a circle, the turning mirror plate part 31 has a circular plate shape.

The orbiting mirror plate unit 31 may be seated on the fixed wrap 42 of the fixed scroll 40 . In addition, the turning mirror plate 31 and the fixing wrap 42 may form a thrust surface.

When the surface facing the front housing 12 is referred to as a first surface and the surface facing the fixed scroll 40 is referred to as a second surface among both surfaces of the orbiting mirror plate unit 31, the ring receiving groove 31a is formed on the first surface. and an orbiting wrap 32 is formed on the second surface.

2 shows an example in which ring receiving grooves 31a are formed on the left and right sides (based on the cross section) of the first surface formed below the turning head plate.

The first surface may be understood as a surface in direct contact with the front housing 12 . Conventionally, a thrust plate was installed between the front housing 12 and the orbiting scroll 30, but there was a problem in that an impact was applied to the anti-rotation pin 71 due to the inner diameter of the hole of the thrust plate.

In the present invention, the front housing 12 directly rubs against the first surface of the turning mirror plate 31 so that the anti-rotation pin 71 can be deeply embedded in the anti-rotation ring 72 as much as the thickness of the existing thrust plate, As the distance from the location where the force is generated is reduced, the moment load is reduced.

A plurality of ring accommodating grooves 31a may be formed to be spaced apart from each other in the circumferential direction in the orbiting mirror plate portion 31 of the orbiting scroll 30 . 6 shows an example in which six ring accommodating grooves 31a are formed and the six ring accommodating grooves 31a are spaced apart in the circumferential direction.

The anti-rotation ring 72 may be coupled to the ring receiving groove 31a by a sliding method so that a predetermined tolerance exists. However, it is not necessarily limited to such a coupling method by a sliding method, and may be coupled by a coupling method other than press-fitting, screw coupling, and the like.

In the anti-rotation ring 72 coupled to the ring receiving groove 31a, an anti-rotation pin 71, which will be described later, can be pivotally installed. The anti-rotation ring 72 is made to rotate relative to the anti-rotation pin 71 .

The ring receiving groove 31a may be formed in a circular shape with a closed periphery, and in some cases may be formed in an arc shape with a portion of the periphery open. Referring to FIG. 6, in this embodiment, an example in which the ring receiving groove 31a is formed in a circular shape is shown.

Due to the structure of the anti-rotation pin 71 and the anti-rotation ring 72, the orbiting scroll 30 can rotate while preventing rotation between the front housing 12 and the fixed scroll 40.

The orbiting wrap 32 forms an involute curve, an arithmetic spiral (Archimedean spiral) or a logarithmic spiral (logarithmic spiral) from the second surface of the orbiting head plate 31 toward the fixed scroll 40. protrudes into shape. The orbiting wrap 32 may be formed in various other shapes.

The orbiting wrap 32 may be in close contact with the fixed end plate 41 . Similarly, the fixing wrap 42 may also adhere to the turning mirror plate 31 . At least one of the axial end of the stationary wrap 42 and the axial end of the orbiting wrap 32 is provided with a tip chamber to seal the compression chamber V.

A shaft coupling portion 33 is formed at the center of the turning mirror plate portion 31 . The shaft coupling portion 33 protrudes toward the fixed scroll 40 from the first surface of the orbiting mirror plate portion 31 . The shaft coupling part 33 may be formed at a position corresponding to the base circle of the involute shape defining the orbiting wrap 32 . Accordingly, the shaft coupling part 33 forms the innermost part of the orbiting wrap 32 .

The orbiting wrap 32 may extend to an outer circumferential surface of the orbiting head plate 31 . Due to this, it is possible to maximize the suction volume by maximally extending the wrap length of the orbiting wrap 32 .

In addition, the shaft coupling portion 33 may be formed in a cylindrical shape to accommodate the eccentric bush 25 installed on the rotation shaft 20 . Alternatively, the shaft coupling portion 33 may be understood as a boss shape. The shaft coupling portion 33 is formed to surround the eccentric bush 25 installed on the rotation shaft 20 .

A third bearing may be provided between the inner circumferential surface of the shaft coupling part 33 and the outer circumferential surface of the eccentric bush 25 . Referring to FIG. 2, the third bearing is illustrated as an example consisting of a needle bearing, but is not necessarily limited thereto, and may be a bushing bearing or a ball bearing.

The fixed scroll 40 and the orbiting scroll 30 are coupled to each other to form a pair of compression chambers (V). As the orbiting scroll 30 orbits, the volume of the compression chamber V repeatedly fluctuates, and accordingly, a fluid such as a refrigerant is compressed in the compression chamber V.

The fixed scroll 40 is disposed relatively far from the transmission unit (not shown), and the orbiting scroll 30 is disposed relatively close to the transmission unit. The fixed scroll 40 is disposed between the orbiting scroll 30 and the main housing 1110 in the axial direction. In addition, the orbiting scroll 30 is disposed between the fixed scroll 40 and the front housing 12 in the axial direction.

The scroll compressor 100 of the present invention may further include a middle housing 11 . In addition, the scroll compressor of the present invention may further include a rear housing 13.

The aforementioned front housing 12, middle housing 11, and rear housing 13 may form a housing constituting an external appearance of the scroll compressor 100 of the present invention. That is, the housing of the scroll compressor 100 of the present invention may be formed to include the front housing 12, the middle housing 11 and the rear housing 13.

The fixed scroll 40 is supported by the middle housing 11 in the radial direction of the rotating shaft 20 . And, the fixed scroll 40 is supported by the rear housing 13 in the axial direction of the rotating shaft 20 .

The orbiting scroll 30 and the fixed scroll 40 are disposed to face each other. The orbiting scroll 30 is coupled to the eccentric bush 25 of the rotary shaft 20 . Accordingly, the orbiting scroll 30 is eccentrically coupled to the rotating shaft 20 and rotates eccentrically rather than concentrically. That is, the orbiting scroll 30 is coupled with the eccentric bush 25 to receive rotational force through the eccentric bush 25, and the orbiting scroll 30 is guided to prevent rotation by the anti-rotation member 70, turning motion is possible.

In this way, the fixed scroll 40 is disposed to face the orbiting scroll 30. Since the orbiting scroll 30 is axially supported by the front housing 12, the fixed scroll 40 also moves in the axial direction. It can be understood as a structure indirectly supported by the front housing 12 .

The fixed scroll 40 includes a fixed end plate 41 and a fixed wrap 42 .

The fixed end plate 41 has an O-ring between the outer circumferential surface and the inner circumferential surface of the middle housing 11 to separate high and low pressure. Referring to FIG. 2 , the upper portion of the fixed head plate 41 is supported by the rear housing 13 . In addition, the fixed end plate portion 41 is formed in a plate shape. The fixed head plate portion 41 may have a circular cross section, in which case the fixed head plate portion 41 has a disk shape.

If the surface facing the rear housing 13 of both surfaces of the fixed head plate 41 is referred to as a first surface and the surface facing the orbiting scroll 30 is referred to as a second surface, the first surface has a partition protrusion 41c And a bypass guide groove 41c-1 is formed, and a fixing wrap 42 is formed on the second surface.

The fixed wrap 42 protrudes toward the orbiting scroll 30 in the shape of an involute curve, an arithmetic spiral (Archimedean spiral) or a logarithmic spiral (logarithmic spiral). The fixing wrap 42 may be formed in various other shapes. The stationary wrap 42 is engaged with the orbiting wrap 32 to form a compression chamber V.

A discharge port 411 is formed at the center of the fixed end plate 41 . Referring to FIG. 2 , in this embodiment, an example in which one discharge port 411 is formed at the center of the fixed end plate 41 is shown.

At least one or more bypass holes 412a and 412b may be formed around the discharge port 411 .

For example, the bypass holes 412a and 412b may include a first bypass hole 412a for preventing overcompression to prevent overcompression and/or a second bypass hole 412b for variable capacity for variable capacity.

The first bypass hole 412a may be formed independently for each compression chamber V in the vicinity of the discharge port 411 .

In addition, the second bypass hole 412b may be formed independently for each compression chamber V at a position farther from the discharge port 411 than the first bypass hole 412a.

The outlet 411, the first bypass hole 412a, and the second bypass hole 412b may be opened and closed by valves, respectively. For example, the discharge port 411 is operated by the discharge valve 45, the first bypass hole 412a is operated by the first bypass valve 46, and the second bypass hole 412b is operated by the second bypass valve. It can be opened and closed by (47).

The discharge valve 45, the first bypass valve 46, and the second bypass valve 47 may be configured independently, or some may be connected to each other and integrally formed. In this embodiment, the discharge valve 45, the first bypass valve 46, and the second bypass valve 47 may be independently formed and combined.

On the other hand, a discharge space 10b is formed between the rear surface of the fixed head plate 41 and the inner space of the rear housing 13 facing it, and the discharge space 10b is formed between the first discharge space 10b1 and the second discharge space 10b. It can be separated by the discharge space 10b2. For example, a partition protrusion 41c extending toward the rear housing 13 by a predetermined height may be formed on the rear surface of the fixed head plate portion 41 .

The partition protrusion 41c is formed in a substantially V-shaped ring shape when projected in the axial direction to separate the first discharge space 10b1 and the second discharge space 10b2. For example, the first discharge space 10b1 may be formed outside the partition protrusion 41c and the second discharge space 10b2 may be formed inside the partition protrusion 41c.

The first discharge space 10b1 may communicate with the refrigerant discharge port 13a described above, and the second discharge space 10b2 may communicate with the bypass port 13b described above. The discharge valve 45 and the first bypass valve 46 belong to the first discharge space 10b1, and the second bypass valve 47 belongs to the second discharge space 10b2. Accordingly, in the first discharge space 10b1, the refrigerant discharged from the discharge pressure chambers (unsigned) of both compression chambers (V) or bypassed from the first intermediate pressure chamber (unmarked) of both compression chambers (V) will be described later. Through the refrigerant discharge pipe 116, it forms a substantial discharge space that guides the condenser 20 of the refrigerant cycle, and the second discharge space 10b2 is an intermediate pressure chamber (lower pressure than the first intermediate pressure chamber) of both compression chambers V. A kind of bypass space is formed in which the refrigerant bypassed in the second intermediate pressure chamber is recovered to the suction space 110a of the casing 110 through the refrigerant recovery pipe 151 to be described later.

The partition protrusion 41c may be formed only on the fixed head plate portion 41, but may also be formed on the front surface of the rear housing 13 facing the fixed head plate portion 41 in some cases.

For example, the first partitioning protrusion (for convenience, the reference numeral of the partitioning protrusion) 41c is on the rear surface of the fixed head plate 41, and the second partitioning protrusion 13c is on the front surface of the rear housing 13. They may be formed to correspond to each other.

A bypass guide groove 41c-1 is formed inside the partition protrusion 41c. The bypass guide groove 41c-1 is formed in a substantially V-shape to accommodate the second bypass holes 412b of both compression chambers V together. When the partition protrusion is divided into the first partition protrusion 41c and the second partition protrusion 13c, the bypass guide groove 41c-1 is formed in the first partition protrusion 41c and the second partition protrusion 13c, respectively. It may be, or it may be formed only on one of the partition protrusions.

2 shows an example in which the bypass guide groove 41c-1 is formed in the first partition protrusion 41c.

The rotating shaft 20 is rotated by the generated power, and transmits this rotational force to the orbiting scroll 30 so that the orbiting scroll 30 can orbitally rotate.

For example, the rotating shaft 20 is rotated by power transmitted through the clutch assembly 2 and may transmit the rotational force to the orbiting scroll 30 .

The rotating shaft 20 is rotatably installed on the inner circumference of the front housing 12 . In addition, the rotating shaft 20 is installed in the shaft coupling portion 33 of the orbiting scroll 30 to enable the orbiting scroll 30 to orbitally rotate.

Preferably, the rotating shaft 20 may be concentrically disposed on the front housing 12 .

The rotating shaft 20 may be supported by first and second bearings 85 and 86 to be described later.

An eccentric bush 25 may be installed on the rotary shaft 20 to enable the orbiting scroll 30 to orbitally rotate. To this end, a coupling pin 22 to which the eccentric bush 25 is coupled may be provided at an end of the rotary shaft 20 toward the orbiting scroll 30 .

The eccentric bush 25 has a coupling hole into which the coupling pin 22 is inserted so as to be eccentric with respect to the center of the eccentric bush 25 .

The coupling pin 22 is provided to be eccentric with respect to the center of the rotation shaft 20 at the rear end (top in FIG. 2 ) of the rotation shaft 20 . In addition, an eccentric bush 25 is rotatably installed on the coupling pin 22 .

In addition, the eccentric bush 25 may be provided with a sub-balance weight 25a to help the orbiting scroll 30 rotate. The sub balance weight 25a may be disposed on the outer circumference of the shaft coupling part 33 of the orbiting scroll 30 .

2 shows an example in which the sub balance weight 25a is formed integrally with the eccentric bush 25, but is not necessarily limited thereto, and the sub balance weight 25a is a separate member of the eccentric bush 25 by bolting, etc. It is also possible to combine by the method of.

2, in the orbiting scroll 30, the eccentric bush 25 of the rotating shaft 20 is coupled to the inside of the shaft coupling portion 33, and a sub balance weight 25a is disposed on the outer circumference of the shaft coupling portion 33. An example is shown.

Accordingly, the rotary shaft 20 is rotated by the rotational force transmitted from the clutch assembly 2, and the eccentric bush 25 at the end of the rotary shaft 20 is rotated eccentrically, so that the orbiting scroll 30 can orbitally rotate. .

On the other hand, an oil passage (not shown) may be provided inside the rotary shaft 20, and oil flowing in the oil passage may be supplied to the shaft sealing member 84. To this end, the rotary shaft 20 has a shaft An oil hole or groove may be formed adjacent to the sealing member 84 .

The rear housing 13 is formed in a substantially cylindrical shape with one end (front end) open and the other end (rear end) closed.

In the present invention, as can be seen from the names of the front housing 12 and the rear housing 13, the front housing 12 side is the front side and the rear housing 13 side is the rear side. .

In other words, the front end facing the fixed scroll 40 is open while the rear end facing the fixed scroll 40 is closed.

Accordingly, the inner space of the rear housing 13 forms a discharge space 10b together with the rear surface of the fixed end plate 41 to be described later, so that the refrigerant discharged from the compression chamber V is accommodated.

At the front end of the rear housing 13, a rear flange portion 13a, which is bolted to the aforementioned middle flange portion 11d, extends in a flange shape. The second sealing member 82 described above is inserted between the rear flange portion 13a and the middle flange portion 11d and fastened with bolts along the circumferential direction.

A third connection protrusion (unsigned) and a fourth connection protrusion (unsigned) are formed at the closed rear end of the rear housing 13. The third connection protrusion is formed at the center of the rear end of the rear housing 13, and the fourth connection protrusion is formed around the third connection protrusion. A refrigerant discharge port 13a is formed in the third connection protrusion, and a bypass port 13b is formed in the fourth connection protrusion. The refrigerant discharge port 13a and the bypass port 13b are formed penetrating between the inner and outer surfaces of the rear housing 13, respectively.

The front housing 12 supports the orbiting scroll 30 so as to be able to orbitally rotate.

For example, the front housing 12 may support the second surface where the ring receiving groove 31a of the orbiting scroll 30 is formed.

The front housing 12 may be disposed between the clutch assembly 2 and the orbiting scroll 30 .

The front housing 12 may be formed of a cast iron material. Since the front housing 12 is formed of a cast iron material, when the scroll compressor 100 of the present invention is applied to a commercial heat pump, the load is relatively large and the movement of the compressor is relatively large compared to the case where it is applied to an automobile air conditioning compressor. It is advantageous in terms of reliability because it is not necessary.

Meanwhile, the front housing 12 is usually made of an aluminum-based material to reduce the weight of the compressor when applied to a vehicle.

However, as in the present invention, for example, as the compressor applied to building air conditioning is fixedly installed in an outdoor unit, the front housing 12 may be made of cast iron material instead of aluminum material, and thus the load is greater than that of vehicles. The reliability of compressors for building air conditioning can be improved.

Meanwhile, the front housing 12 is coupled to the front end of the middle housing 11 to seal the suction space, which is the inner space of the middle housing 11, while supporting the orbiting scroll 30 in the axial direction. In this way, the front housing 12, while forming a part of the housing, also functions as a frame constituting the compression portion.

In the present invention, as described above, the orbiting scroll 30 may be formed of aluminum or aluminum alloy, and the front housing 12 is formed of a casting material and is formed of a different material, so that the orbiting scroll 30 and the front The housing 12 can directly rub against each other and has a structure that does not require a separate thrust plate between the orbiting scroll 30 and the front housing 12 .

Accordingly, it is possible to prevent an impact from being applied due to contact between the inner diameter of the hole provided in the existing thrust plate and the anti-rotation pin 71 .

In addition, since the anti-rotation pin 71 can be driven deeper by the thickness of the thrust plate, the distance from the position where the force is generated is reduced, thereby reducing the moment load.

In this way, the orbiting scroll 30 is formed of a different material from the front housing 12 to form a structure capable of direct friction between the orbiting scroll 30 and the front housing 12, and separate thrust between the two. The reliability of the pin-and-ring structure can be improved because the plate is not required.

9 is a perspective view schematically showing an anti-rotation pin 71 among pins and rings in the present invention, and FIG. 10 shows a structural analysis result of an anti-rotation pin 71 installed in a front housing 12 of a conventional structure. 11 is a conceptual diagram showing the structural analysis result of the anti-rotation pin 71 installed in the front housing 12 in the present invention.

As a result of structural analysis under the above conditions, it was confirmed that the stress of the root portion of the anti-rotation pin 71 was improved by 11.4% compared to the prior art.

Referring to FIG. 9 , the length of the pin load in the anti-rotation pin 71 is the length of the anti-rotation pin 71 at the portion to which the load is applied, and is indicated by section a in FIG. 10 . In addition, in FIG. 10 , the portion where the thrust plate is seated is indicated as section b, and the length at which the anti-rotation pin 71 is driven into the front housing 12 is indicated as section c.

9 can be understood as a boundary condition for structural analysis, and the load applied to both ends of the anti-rotation pin 71 is 500 N.

In the case of the prior art provided with a thrust plate, of the total length of the anti-rotation pin 71, the pin load length (a) where the load is applied to the anti-rotation pin (71), the length (b) where the thrust plate is seated, and the rotation The length (c) in which the prevention pin 71 is driven into the front housing 12 is disclosed.

On the other hand, in the present invention, of the total length of the anti-rotation pin 71, the pin load length (a) where the load is applied to the anti-rotation pin 71, and the length (b) where the thrust plate is seated because the thrust plate is not provided , the length (c) that the anti-rotation pin 71 is driven into the front housing 12 is disclosed.

In particular, since the thrust plate is not provided, the length b on which the thrust plate is seated does not exist.

On the other hand, referring to FIGS. 10 and 11, looking at the structural analysis results, the maximum stress applied to the anti-rotation pin 71 is when the conventional thrust plate is installed between the front housing 12 and the orbiting scroll 30 It was 102 Mpa (100%), but when the thrust plate of the present invention is not installed and the front housing 12 and the orbiting scroll 30 are in direct contact, it becomes 90.4 Mpa (88.6%), reducing the stress by 11.4% There is an improvement effect.

Hereinafter, the detailed configuration of the front housing 12 will be described.

The front housing 12 may include a housing flange portion 12a and a support wall portion 12b.

One side of the housing flange portion 12a faces the clutch assembly 2 and the other side faces the orbiting scroll 30.

Further, the housing flange portion 12a is coupled to the middle flange portion 11d of the middle housing 11, so that the front housing 12 rotates the turning scroll 30 while being fixedly supported by the middle housing 11. It is supported so that it can rotate.

In addition, as described above, the housing flange portion 12a may form a part of the outside of the compressor and function as a part of the housing.

Further, the housing flange portion 12a has a flange shape extending radially from the outer periphery of the front housing 12 . For example, the housing flange portion 12a may have a circular cross section, in which case the housing flange portion 12a has a circular plate shape.

In addition, the front housing 12 may be provided with shaft coupling portions 12d and 12f. A first shaft coupling portion 12d may be provided at a front end (lower side with reference to FIG. 2 ) of the front housing 12 . The rotation shaft 20 may be installed in the first shaft coupling part 12d.

The shaft coupling portions 12d and 12f may include a first shaft coupling portion 12d with a small inner diameter on the front side and a second shaft coupling portion 12f with a large inner diameter on the rear side.

The first shaft coupling portion 12d may have a small inner diameter, and the second shaft coupling portion 12f may have a large inner diameter.

Referring to FIG. 2 , an example in which the support wall portion 12b of the front housing 12 includes first and second shaft coupling portions 12d and 12f is shown.

In addition, first and second bearings 85 and 86 may be installed in the first and second shaft coupling portions 12d and 12f.

As shown in FIG. 2, the first and second bearings 85 and 86 may be ball bearings, but are not necessarily limited thereto, and may be needle bearings or bushing bearings.

In addition, the orbiting scroll 30 is disposed adjacent to the second bearing 86, and as the vibration caused by the rotation of the orbiting scroll 30 is transmitted, the second bearing 86 has a load bearing capacity greater than that of the first bearing 85. This can be made with large bearings.

As shown in FIG. 2 , the lower part (front side) of the rotary shaft 20 is supported by the first bearing 85 and the upper part of the rotary shaft 20 is supported by the second bearing 86 .

Meanwhile, between the first and second bearings 85 and 86 in the axial direction, a shaft sealing member 84 may be installed on the rotating shaft 20 . The shaft sealing member 84 may be installed between the rotating shaft 20 and the inner circumference of the front housing 12, and seals the front of the suction space.

The shaft sealing member 84 may include a fixed sealing part 84a and a movable sealing part 84b.

The fixed sealing part 84a is fixedly coupled to the inner circumferential surface of the shaft coupling part 12d provided in the front of the front housing 12, and the movable sealing part 1842 rotates the shaft 20 in the lubrication space part 12d-1. It may be coupled to the outer circumferential surface of the rotating shaft 20 to rotate together.

Accordingly, when the rotating shaft 20 rotates, the movable sealing part 1842 is in close contact with the fixed sealing part 84a, and the shaft accommodating part 12e provided in front of the front housing 12 and the lubrication space part 12d-1 ), that is, to seal the front side of the suction space 10a.

A support wall portion 12b may be formed on a surface of the housing flange portion 12a facing the orbiting scroll 30 .

The support wall portion 12b may protrude from a surface of the housing flange portion 12a facing the orbiting scroll 30 .

In addition, the supporting wall portion 12b may be formed in a cylindrical structure with both ends open.

A rotational shaft 20 that transmits a rotational force to the orbiting scroll 30 may be accommodated inside the support wall 12b.

In addition, an orbiting space 12b-1 is provided on the inner circumference of the support wall 12b, and the orbiting space 12b-1 is a space in which the coupling part 33 of the orbiting scroll 30 performs a pivoting motion, and is used for shaft water. It may be formed to communicate with an internal space such as a unit.

The diameter of the outer circumference of the supporting wall portion 12b should be larger than the diameter of the turning mirror plate portion 31. In addition, it is preferable that the support wall portion 12b has a predetermined width so as to maintain rigidity sufficient to support the orbiting scroll 30 so as to be able to orbitally rotate.

The support wall portion 12b may be disposed inside a predetermined distance in a radial direction from the outer circumference of the housing flange portion 12a.

Also, the outer circumferential surface of the supporting wall portion 12b is in close contact with the inner circumferential surface of the middle housing 11 . Accordingly, the housing flange portion 12a may be fixed to the inside of the middle housing 11 .

The support wall part 12b is provided with the turning contact surface 12a-1 with which the turning scroll 30 directly rubs and contacts so that turning rotation is possible. In FIG. 4 and the like, the pivot contact surface 12a-1 is provided on the upper surface of the support wall portion 12b, and the pivot contact surface 12a-1 can be understood as being formed on the “rear surface” of the support wall portion 12b. .

The orbiting contact surface 12a-1 of the supporting wall 12b supports the orbiting mirror plate 31 of the orbiting scroll 30 in the axial direction and forms an axial bearing surface.

Conventionally, a thrust plate was installed between the front housing 12 and the orbiting scroll 30, but there was a problem in that an impact was applied to the anti-rotation pin 71 due to the inner diameter of the hole of the thrust plate.

In the present invention, a structure in which the orbiting contact surface 12a-1 provided on the support wall 12b of the front housing 12 directly rubs against the second surface of the orbiting scroll 30 is formed.

The supporting wall portion 12b of the front housing 12 supports the orbiting scroll 30 in the axial direction. As such, the support wall portion 12b may form part of the compression portion.

The orbiting contact surface 12a-1 is a surface that directly rubs against the orbiting scroll 30, has wear resistance to maintain reliability even in repetitive orbital movements of the orbiting scroll 30, and has a surface roughness greater than or equal to a predetermined value. should have

Due to this, since the anti-rotation pin 71 can be deeply embedded in the anti-rotation ring 72 as much as the thickness of the existing thrust plate, the distance from the position where the force is generated is reduced, thereby reducing the moment load.

In addition, with this structure, it is possible to reduce the number of parts, thereby simplifying the structure, reducing material cost, and improving assemblability.

Meanwhile, an anti-rotation pin 71 and an oil supply groove 12c may be formed on the pivot contact surface 12a-1, which will be described later.

Meanwhile, as shown in FIG. 2 , the support wall portion 12b may be inserted into the inner circumference of the middle housing 11 . Also, the front housing 12 may be coupled to the middle housing 11 by shrinking or welding.

Further, the support wall portion 12b may be integrally formed with the housing flange portion 12a. However, it is not necessarily limited thereto, and the support wall portion 12b may be formed as a separate member from the housing flange portion 12a and coupled to each other by bolts or the like. In this case, the aforementioned first and second bearings 85 and 86 and the shaft sealing member 84 can be easily assembled.

The rotation preventing member 70 is formed to rotate the orbiting scroll 30 while preventing the rotation of the orbiting scroll 30 . If there is no anti-rotation member 70, the orbiting scroll 30 will be rotated by the driving force transmitted by the rotating shaft 20. That is, the rotation of the orbiting scroll 30 is prevented by the rotation prevention member 70 and the orbiting scroll 30 is allowed to orbit.

The anti-rotation member 70 may include an anti-rotation pin 71 and an anti-rotation ring 72 . Each of the anti-rotation pin 71 and the anti-rotation ring 72 may be provided in plurality. Referring to FIGS. 3 and 5 , as shown, six anti-rotation pins 71 and six anti-rotation rings 72 may be provided. However, it is not limited thereto, and the anti-rotation pin 71 and the anti-rotation ring 72 may be provided in different numbers.

Hereinafter, the structure of the anti-rotation pin 71 and the anti-rotation ring 72 will be described in more detail.

An anti-rotation pin 71 protruding toward the orbiting scroll 30 is provided on the orbiting contact surface 12a-1.

The anti-rotation pin 71 may be provided as a separate member. In this case, a pin coupling hole 12a-2 to which the anti-rotation pin 71 is coupled may be formed in the pivot contact surface 12a-1. A plurality of pin coupling holes 12a-2 are formed to couple the anti-rotation pins 71, and the plurality of pin coupling holes 12a-2 may be spaced apart from each other in a circumferential direction.

However, it is not necessarily limited to the structure in which the anti-rotation pin 71 is installed as a separate member, and the anti-rotation pin 71 may be formed integrally with the pivot contact surface 12a-1.

An oil supply groove 12c, which will be described later, may be provided between the pivoting contact surface 12a-1 and the anti-rotation pin 71.

On the other hand, in the anti-rotation ring 72 coupled to the ring receiving groove 31a of the orbiting scroll 30 described above, the anti-rotation pin 71 provided on the orbiting contact surface 12a-1 is installed to be able to pivot. can The anti-rotation ring 72 is made to rotate relative to the anti-rotation pin 71 .

The anti-rotation ring 72 performs a rotational motion like the orbiting scroll 30 while preventing rotation in a radial direction by the anti-rotation pin 71 .

The anti-rotation ring 72 is fixedly or rotatably inserted into the ring receiving groove 31a. In addition, the anti-rotation pin 71 is slidably inserted into the anti-rotation ring 72 from the inner circumference of the anti-rotation ring 72 along the circumferential direction. The anti-rotation ring 72 may have the shape of a circular ring or may have a C-shaped shape with one side open. In the present invention, an example formed in the shape of a circular ring similarly to the ring receiving groove 31a will be described.

At this time, the diameter (d _pin ) of the anti-rotation pin 71 has a correlation with the inner diameter (r _i ) of the anti-rotation ring 72, and the inner diameter (r _i ) of the anti-rotation ring 72 is 2 * The turning radius (ε) + diameter (d _pin ) of the anti-rotation pin 71 must be satisfied to have the anti-rotation function (ie, r _i = 2 *ε + d _pin ).

Due to the structure of the anti-rotation pin 71 and the anti-rotation ring 72, the orbiting scroll 30 can orbitally rotate between the front housing 12 and the fixed scroll 40.

Meanwhile, an oil supply groove 12c capable of supplying oil to a surface between the front housing 12 and the orbiting scroll 30 may be formed in the support wall portion 12b.

The oil supply groove 12c may be formed concavely in the pivoting contact surface 12a-1 of the support wall 12b.

The oil supply groove 12c may be formed in at least one of a circumferential direction and a radial direction intersecting with the circumferential direction of the turning contact surface 12a-1.

Due to this, the oil accommodated in the inner circumference of the housing can flow in the orbiting contact surface 12a-1 through the oil supply groove 12c of the front housing 12 according to the rotation of the orbiting scroll 30. And, oil supply is possible between the front housing 12 and the orbiting scroll 30 to improve reliability.

A suction space is provided inside the housing, and the oil storage space forms a lower half of the suction space. Oil is stored in the oil storage space, and oil can be supplied between the front housing 12 and the orbiting scroll 30 through the oil supply groove 12c.

Meanwhile, the oil may be oil supplied from an oil recovery device that separates the oil from the refrigerant discharged from the compression chamber V and returns it to the compressor.

For example, the oil supply groove 12c may include first and second oil supply grooves 12c-1 and 12c-2.

The first oil supply groove 12c-1 may be formed in the radial direction on the orbiting contact surface 12a-1, so that the rotation of the orbiting scroll 30 enables oil to flow in the radial direction.

In addition, a plurality of first oil supply grooves 12c-1 may be formed, and the plurality of first oil supply grooves 12c-1 may be spaced apart from each other in a circumferential direction.

3 and 5, six first oil supply grooves 12c-1 are formed in a radial direction, and each of the first oil supply grooves 12c-1 is spaced apart at equal intervals along the circumferential direction. An example of the arrangement is shown.

In addition, each of the first oil supply grooves 12c-1 may be formed from the inner circumference to the outer circumference of the front housing 12 on the pivot contact surface 12a-1. The first oil supply groove 12c-1 may be formed through the inner and outer circumferences of the front housing 12 at the pivot contact surface 12a-1. 5 to 7, the first oil supply groove 12c-1 includes an inner end groove 12c-4 formed on the inner circumference of the front housing 12 and an outer end groove formed on the outer circumference of the front housing 12. 12c-3, the first oil supply groove 12c-1 is formed through the inner and outer circumferences of the support wall 12b of the front housing 12 at the pivot contact surface 12a-1.

Due to the structure in which the inner end groove 12c-4 and the outer end groove 12c-3 are formed, oil on the outer circumference or inner periphery of the front housing 12 can flow to the inner periphery or outer circumference of the front housing 12, and the rotation Oil can also be more sufficiently supplied to the contact surface 12a-1.

In addition, the front housing 12 has the pivoting contact surface 12a-1 at an end and a support wall portion 12b extending in the extension direction of the rotation shaft 20, although not shown in the drawings. , The first oil supply groove (12c-1) is formed so that both ends are spaced apart from each other on the inner and outer circumferences of the support wall portion (12b) and may not penetrate the inner and outer circumferences of the support wall portion (12b).

The structure in which the outer or inner circumferential surfaces of both ends of the first oil supply groove 12c-1 are blocked is advantageous for oil storage.

A first oil supply path, which is a space through which oil can flow in a radial direction, may be provided inside the first oil supply groove 12c-1.

Meanwhile, the second oil supply groove 12c-2 may be formed in the circumferential direction on the orbiting contact surface 12a-1, enabling oil to flow in the circumferential direction by rotation of the orbiting scroll 30.

For example, the second oil supply groove 12c-2 may be formed in a circular shape on the pivoting contact surface 12a-1. In addition, the second oil supply groove (12c-2) is formed to communicate with each other by crossing the first oil supply groove (12c-1), so that the oil flowing in the first oil supply groove (12c-1) flows into the second oil supply groove (12c-1). 2), and conversely, the oil flowing in the second oil supply groove 12c-2 may be provided to the first oil supply groove 12c-1.

A plurality of second oil supply grooves 12c-2 are formed, and an intersection end portion communicating with the first oil supply groove 12c-1 is provided at an end in the circumferential direction of each second oil supply groove 12c-2. It can be.

Referring to FIGS. 7 and 8 , an example in which six second oil supply grooves 12c-2 are formed and a cross section is provided between each second oil supply groove 12c-2 is shown.

In addition, the second oil supply groove 12c-2 may allow a plurality of first oil supply grooves 12c-1 spaced apart from each other to communicate with each other.

In addition, the second oil supply groove 12c-2 may be formed in the circumferential direction between the inner end groove 12c-4 and the outer end groove 12c-3 of the first oil supply groove 12c-1. Referring to FIG. 7 , an example in which the inner end groove 12c-4 and the outer end groove 12c-3 are formed in a circular shape at the center is shown.

Due to the structure of the first and second oil supply grooves 12c-1 and 12c-2, oil can flow in the radial and circumferential directions on the pivoting contact surface 12a-1 of the front housing 12, Reliability can be improved between the front housing 12 and the orbiting scroll 30 .

The present invention, as the oil supply groove 12c is formed on the orbiting contact surface 12a-1 of the front housing 12, the anti-rotation ring, which occurred in the structure in which the oil groove is formed in the conventional orbiting scroll 30 The problem of interference between the ring groove and the oil groove to be installed does not occur.

On the other hand, as described above, the oil supply groove 12c is formed in the pivot contact surface 12a-1. The oil supply groove 12c is formed concavely in the pivoting contact surface 12a-1, although not shown in the drawing, the first oil supply groove 12c-1 is not included, and the second oil supply groove 12c-2 is not included. ) are also possible.

In addition, the oil supply groove communicates with the second oil supply groove 12c-2 to guide oil to the second oil supply groove 12c-2 and communicates with the second oil supply groove 12c-2 in the radial direction. It may further include a third oil refueling groove. The second oil supply groove 12c-2 may be formed in a radial direction from the lower half toward the storage space. The third oil supply groove may have the same or similar shape as the first oil supply groove described above.

In the present invention, in the lower half, when the front housing 12 side is the front side and the rear housing 13 side is the rear side, the oil is stored between the front housing 12 and the rear housing 13 based on the portion. , means the side where the oil storage space where oil is stored is disposed, and the upper half means one side opposite to the side where the oil storage space where oil is stored is disposed between the front housing 12 and the rear housing 13 .

In the present invention, the first to third oil supply grooves may have a wide width for the oil supply grooves disposed in the lower half to further improve the flow of oil disposed in the lower half, and conversely, the oil supply grooves disposed in the upper half may have a narrow width. there is.

The scroll compressor 100 of the present invention may further include a clutch assembly 2 .

The clutch assembly 2 may include a clutch plate 2a, a pulley 2b, and a coil unit 2c.

The clutch plate 2a, when power is applied to an external transmission unit (not shown) and the transmission unit is driven, the clutch plate 2a connected thereto is driven, including the pulley 2b and the coil unit 2c. It enables the operation of the clutch assembly (2).

The pulley 2b may be rotated by receiving power generated from an external transmission unit.

A belt or the like may be installed on the pulley 2b so that power generated from the outside can be transmitted. The rotating shaft 20 is rotated by the rotation of the pulley 2b, so that the turning scroll 30 can be turned and rotated.

For example, the pulley 2b of the clutch assembly 2 may be rotated by transmitting power generated from an external transmission unit by the pulley 2b coupled to the external transmission unit. In this case, the pulley coupled to the external transmission unit is a driving pulley directly rotated by the external transmission unit, and the pulley 2b of the clutch assembly 2 is connected to the driving pulley 2b by a belt and rotates indirectly. It can be understood as a homogeneous pulley (2b) to do.

Hereinafter, the operation of the scroll compressor 100 according to the present invention will be described.

That is, when operation of the gas engine heat pump configured such that the scroll compressor, the condenser, the expander, and the evaporator form a closed loop is selected, the clutch assembly 2 transmits the driving force to the rotary shaft 20 . The driving force transmitted to the rotating shaft 20 is transmitted to the orbiting scroll 30 through the rotating shaft 20 .

Then, in a state where the orbiting scroll 30 is supported by the front housing 12, it orbits as much as the eccentric distance of the eccentric bush 25, and at the same time, a suction chamber is placed between the orbiting wrap 32 and the stationary wrap 42. , an intermediate pressure chamber, and two pairs of compression chambers (V) consisting of a discharge chamber are formed in succession. The volume of the compression chamber (V) is reduced while moving toward the center by the continuous turning motion of the orbiting scroll (30), and the refrigerant is compressed while moving along the compression chamber (V) through the discharge port (411) to the discharge space (10b). ), that is, discharged into the first discharge space 10b1 of FIG. 2 .

At this time, the thrust plate conventionally provided between the orbiting scroll 30 and the front housing 12 is removed, and the front housing 12 and the orbiting scroll 30 are directly rubbed to cause relative movement, thereby causing the front housing to An impact applied between 12 and the orbiting scroll 30 is alleviated, and a moment load applied to the anti-rotation pin is reduced, so reliability between the front housing 12 and the orbiting scroll 30 can be improved.

In addition, in the present invention, since the front housing 12 directly rubs against the second surface of the orbiting scroll 30 so that the pin can be deeply embedded in the front housing as much as the thickness of the existing thrust plate, the distance from the position where the force is generated is reduced and the moment load is reduced.

In particular, since the orbiting scroll 30 may be formed of aluminum, and the front housing 12 is formed of a cast iron material and is formed of a different material, the orbiting scroll 30 is formed of a different material from the front housing 12, , A structure capable of direct friction between the orbiting scroll 30 and the front housing 12 is formed, and a separate thrust plate is not required between the two, so the reliability of the pin-and-ring structure can be improved.

At this time, the refrigerant in the compression chamber (V) is compressed to a set pressure while moving from the intermediate pressure chamber to the discharge pressure chamber. can rise to Then, part of the refrigerant moving from the intermediate pressure chamber to the discharge pressure chamber passes through the first bypass hole 412a before reaching the discharge pressure chamber in each compression chamber V to the discharge space 10b, precisely the first discharge space ( 10b1) is bypassed in advance.

Through this, it is possible to suppress the refrigerant from being overcompressed to a set pressure or higher in both compression chambers (V), thereby increasing compressor efficiency and securing stability of the orbiting wrap 32 and the stationary wrap 42 constituting the compression part.

In addition, the gas engine heat pump including the compressor 10 can vary the operating capacity as needed during operation. For example, in the case of power operation, the first control valve (not shown) of the refrigerant recovery unit (not shown) is closed to secure the maximum suction volume, whereas in the case of saving operation, the first control valve of the refrigerant recovery unit is opened to The suction volume can be reduced to a minimum.

In other words, during the saving operation, as the first control valve opens, the second discharge space 10b2 communicates with the suction space 10a. Then, a part of the refrigerant sucked into the compression chamber V is bypassed to the second discharge space through the second bypass hole 412b. The refrigerant is introduced into the suction space 10a through the refrigerant recovery pipe and the return port 11b due to the pressure difference between the second discharge space 10b2 and the suction space 10a, and the refrigerant flows into the suction space 10a. The air is sucked into both compression chambers V through the first suction end provided at the end and the second suction end provided at the end of the fixing wrap 42 .

The refrigerant discharged into the first discharge space 10b1 through the discharge port 411 and the first bypass hole 412a is supplied by a refrigerant discharge port 13a and a refrigerant discharge pipe (not shown) coupled to the refrigerant discharge port 13a. It is discharged toward the condenser of the refrigerating cycle device through the

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

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

100: scroll compressor
10: housing 10b: discharge space
10b1: first discharge space 10b2: second discharge space
11a: refrigerant intake port 11b: return port
13a: refrigerant discharge port
12: front housing 12a: housing flange portion
12b: support wall portion 12b-1: turning space portion
12a-1: turning contact surface 12a-2: pin coupling hole
12c: oil supply groove 12c-1: first oil supply groove
12c-2: inner single groove 12c-3: outer single groove
12c-2: 2nd oil supply groove
12d: axis coupling part 12d-1: lubrication space part
12e: bearing portion
11: middle housing
13: rear housing 13d: rear flange portion
30: turning scroll 32: turning wrap
V: compression chamber 31: turning mirror plate part
31a: ring receiving groove 33: shaft coupling part
40: fixed scroll 41: fixed mirror plate
411: discharge port 412a: first bypass hole
412b: second bypass hole 42: fixed wrap
41c: partition protrusion 41c-1: bypass guide groove
20: rotation axis 22: coupling pin
25: eccentric bush 25a: sub balance weight
84: Shaft sealing member 70: Rotation prevention member
31a: ring receiving groove 71: anti-rotation pin
72: anti-rotation ring 2: clutch assembly
2a: clutch plate 2b: pulley 2c: coil part
85: first bearing 86: second bearing

Claims (11)

axis of rotation;
an orbiting scroll installed on the rotating shaft to be able to rotate and having a ring receiving groove on one surface thereof;
a fixed scroll engaged with the orbiting scroll to form a compression chamber between the orbiting scroll and the fixed scroll;
A front housing installed on the opposite side of the fixed scroll with the orbiting scroll interposed therebetween and having an orbiting contact surface supporting the orbiting scroll so as to orbitally rotate;
An anti-rotation ring is coupled to the ring receiving groove,
The orbiting contact surface is provided with an anti-rotation pin, at least a part of which is disposed to come into contact with an inner circumference of the anti-rotation ring to guide the orbital rotation of the orbiting scroll,
The scroll compressor of the front housing, wherein the orbiting contact surface is in direct contact with one surface of the orbiting scroll.
According to claim 1,
A concave oil supply groove is formed on the pivoting contact surface,
The oil supply groove is formed in a radial direction and is provided with a plurality of first oil supply grooves spaced apart from each other in a circumferential direction.
According to claim 2,
The oil supply groove,
A scroll compressor further comprising a second oil supply groove provided to cross the first oil supply groove and formed in a circumferential direction.
According to claim 3,
The second oil supply groove is formed in plurality, and a cross end portion communicating with the first oil supply groove is provided at an end portion of the second oil supply groove in a circumferential direction.
According to claim 1,
The scroll compressor wherein the front housing and the orbiting scroll are formed of different materials.
According to claim 5,
The front housing is formed of cast iron, and the orbiting scroll is formed of aluminum.
According to claim 2,
The front housing has, at an end, a support wall portion having the pivot contact surface and extending in the extension direction of the rotation shaft,
The first oiling groove,
An inner end groove penetrating the inner circumference of the support wall portion;
A scroll compressor having an outer end groove passing through an outer circumference of the support wall portion.
According to claim 7,
The oil supply groove,
Further comprising a second oil supply groove provided to cross the first oil supply groove and formed in a circumferential direction,
The second oil supply groove is provided at the center between the inner end groove and the outer end groove in a radial direction.
According to claim 2,
The front housing has, at an end, a support wall portion having the pivot contact surface and extending in the extension direction of the rotation shaft,
The first oil supply groove is formed so that both ends are spaced apart from the inner and outer circumferences of the support wall portion, respectively, and does not penetrate the inner and outer circumferences of the support wall portion.
According to claim 1,
A concave oil supply groove is formed on the pivoting contact surface,
A scroll compressor comprising a second oil supply groove formed in a circumferential direction.
According to claim 10,
The oil supply groove,
The scroll compressor further comprises a third oil supply groove communicating with the second oil supply groove to guide oil to the second oil supply groove and communicating with the second oil supply groove in a radial direction.