KR20130034538A - Scroll compressor - Google Patents

Abstract

PURPOSE: A scroll compressor is provided to prevent damage to an Oldham's ring supporting the rolling movement of a rolling scroll, thereby improving the performance of the compressor. CONSTITUTION: A scroll compressor comprises a fixed scroll(130), a rolling scroll(140), frames(160,170), and a rotary shaft(126), and a driving unit. The rolling scroll includes a rolling wrap forming first and second compressive chambers on inner and outer surfaces by being interlocked with the fixed wrap and roll-moved around the fixed scroll. The frames support the rolling scroll. The rotary shaft includes an eccentric portion in one end and is joined to the rolling scroll so that the eccentric portion is overlapped with the rolling wrap in a radial direction. The driving unit dries the rotary shaft. A rotation prevention member preventing the rotation of the rolling scroll is arranged in the rolling scroll. The rotation prevention member has a yield stress of 300MPa or greater.

Description

[0001] SCROLL COMPRESSOR [0002]

The present invention relates to a scroll compressor.

The scroll compressor includes a fixed scroll having a fixed wrap and a rotating scroll having a swing wrap. Such a scroll compressor is a method of sucking and compressing a refrigerant through a continuous volume change of the compression chamber formed between the fixed wrap and the swing wrap while the swing scroll is rotated on the fixed scroll.

In addition, since the scroll compressor is continuously sucked, compressed and discharged, the scroll compressor has an advantage over other types of compressors in terms of vibration and noise generated during operation.

In the scroll compressor, its behavior is determined by the shape of the fixed wrap and the swing wrap. The stationary wrap and the swiveling wrap may have any shape, but typically have the form of an involute curve that is easy to machine. An involute curve is a curve that corresponds to the trajectory that the end of the yarn draws when unwinding the yarn wound around a base circle of any radius. In the case of using the involute curve, since the thickness of the wrap is constant, the volume change rate is also constant. In order to obtain a sufficient compression ratio, the number of turns of the wrap must be increased, but the size of the compressor is also increased.

On the other hand, the turning scroll is typically a disk-shaped hard plate and the above-described turning wrap is formed on one side of the hard plate. And, the boss is formed on the back surface is not formed the swing wrap is connected to the rotary shaft for driving the swing scroll. This type can form a turning wrap over almost the entire area of the hard plate, so that the diameter of the hard plate portion can be reduced to obtain the same compression ratio, while the action point to which the repelling force of the refrigerant is applied during compression and the offset force for The action points to which the reaction force is applied are axially spaced apart from each other, so that the swinging scroll is tilted in the operation process, thereby increasing the vibration or noise.

As a method for solving such a problem, a so-called axial through scroll compressor has been disclosed in which a point where the rotating shaft and the rotating scroll are coupled is formed on the same surface as the rotating wrap. In this type of compressor, since the action point of the reaction force of the refrigerant and the action point of the reaction force are acted at the same point, it is possible to solve the problem of tilting the scroll scroll.

In the conventional shaft-through scroll compressor as described above, as shown in FIG. 1, the fixed scroll (for example, a frame fixed to the casing) 2 supporting the swing scroll 1 and the swing scroll 1 is provided. The ring-shaped Oldham's ring 3 is provided in order to prevent the rotating scroll 1 from rotating.

As shown in FIG. 2, the old dam ring 3 protrudes from a ring portion 31 having a substantially circular shape fitted to the rear surface of the hard disk portion of the pivoting scroll 1, and upper and lower sides of the ring portion 31, respectively. It consists of a pair of first key 32 and second key 33 which protrude on one side (shown in the drawing, an example of protruding on one side).

The first key 32 protrudes longer than the thickness of the outer circumferential side of the hard disk portion of the pivoting scroll 1 to be formed over the upper end of the side wall of the fixed scroll 4 and the supporting portion of the pivoting scroll 1. The second key 33 is inserted into the first key groove (not shown), and the second key 33 is coupled to the second key groove 11 formed at the outer circumference of the hard plate portion of the pivoting scroll 1.

However, the conventional Oldham ring is formed such that the keys 31 and 32 of the Oldham ring 3 can slide in a direction substantially orthogonal to the rotational direction of the pivoting scroll 1 so that the pivoting scroll As the rotational motion of (1) is suppressed, the keys 32 and 33 of the old dam ring 3 are subjected to a large stress load. Furthermore, the shaft-through scroll compressor is characterized in that the discharge port is formed eccentrically with respect to the shaft center, so that the gas force is generated eccentrically, which causes the keys 32 and 33 of the old dam ring 3 to increase in Z direction moment. It is to be subjected to a greater stress load and there was a problem that the breakage of the old dam ring produced by casting.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor capable of preventing an Oldham ring from being damaged by a load in a shaft-through scroll compressor.

In order to achieve the object of the present invention, a fixed scroll having a fixed wrap; A turning scroll having an orbiting wrap engaged with the fixed wrap to form first and second compression chambers on outer and inner surfaces thereof, the pivoting scroll being pivotal with respect to the fixed scroll; A frame configured to support the swing scroll by being installed on the opposite side of the fixed scroll with the swing scroll interposed therebetween; A rotation shaft having an eccentric portion at one end thereof and coupled to the swing scroll such that the eccentric portion radially overlaps the pivot wrap; And a driving unit for driving the rotating shaft, wherein the rotating scroll further includes a rotating preventing member for preventing rotating of the rotating scroll, and the rotating preventing member is formed such that the scroll compressor has a yield stress of 300 MPa or more. Is provided.

Here, the anti-rotation member may be formed by sintering stainless steel powder.

The first compression chamber is formed between two contact points P1 and P2 formed by contact between the inner surface of the fixed wrap and the outer surface of the pivoting wrap, and the center O of the eccentric portion and the two contact points P1. , When the angle having the larger value among the angles formed by the two lines connecting P2) is α, at least α <360 ° before the start of discharge.

Further, when the inner contact point of the first compression chamber is P3 at the start of discharge and the inner contact point of the first compression chamber is P4 at 150 ° before the discharge starts, the thickness of the fixed wrap decreases from P3 to P4. Will increase.

Further, the distance between the inner circumferential surface of the fixed wrap and the shaft center of the rotary shaft is D _F , the inner contact point of the first compression chamber is P3 at the start of discharge, and the inner contact point of the first compression chamber is P4 at 150 ° before the start of discharge. In the above, D _F increases from P 3 to P 4 and then decreases.

Further, when the distance between the center of the eccentric portion and the outer circumferential surface of the turning wrap is D ₀ , the inner contact point of the first compression chamber is P3 at the start of discharge, and the inner contact point of the first compression chamber is 150 ° before the discharge starts. When P 4, the D _O increases from P 3 to P 4 and then decreases.

In addition, a rotational shaft coupling portion is formed in the center of the rotating scroll, the eccentric portion is coupled to the inside, a protrusion is formed on the inner peripheral surface of the inner end of the fixed wrap, the compression shaft is formed in contact with the protrusion on the outer peripheral surface of the rotating shaft coupling portion A recess is formed.

Here, the rotating shaft, the shaft portion connected to the drive unit; A pin portion formed concentrically with the shaft portion at the end of the shaft portion; And an eccentric bearing eccentrically fitted to the pin portion, wherein the eccentric bearing is rotatably coupled to the rotation shaft coupling portion.

The scroll compressor according to the present invention is produced by sintering a metal powder so that the Olddam ring for preventing the rotating motion of the rotating scroll has a yield stress of 300 MPa or more, so that the gas force is generated eccentrically, thereby turning the rotating scroll. It is possible to prevent damage to the old dam ring to support the compressor can increase the performance.

1 is a cross-sectional view showing a compression unit in a conventional shaft through scroll compressor,
Figure 2 is a perspective view of the old dam ring in the compression unit according to Figure 1,
3 is a cross-sectional view schematically showing one embodiment of the shaft-through scroll compressor according to the present invention;
4 is a partial cutaway view of the compression unit of the embodiment shown in FIG.
5 is an exploded perspective view illustrating the compression unit shown in FIG. 4;
6 is a plan view showing first and second compression chambers immediately after suction and just before discharge in a scroll compressor having an involute-shaped swing wrap and a fixed wrap;
7 is a plan view showing the shape of a swing wrap in a scroll compressor having a swing wrap and a fixed wrap of another involute type;
8 is a plan view showing a turning wrap and a fixed wrap obtained by another envelope;
FIG. 9 is an enlarged plan view of a central portion of FIG. 8; FIG.
FIG. 10 is a plan view showing a state in which the turning wrap is in a 150 ° position before discharge starts in the embodiment shown in FIG. 8;
11 is a plan view showing a time point at which discharge is started in the second compression chamber in the embodiment shown in FIG. 8;
Figure 12 is a graph shown to explain the technical background that requires the Oldham ring according to the present embodiment.

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

Referring to FIG. 3, the scroll compressor according to the present embodiment includes a cylindrical casing 110 and an upper shell 112 and a lower shell 114 covering upper and lower portions of the casing, respectively. The upper shell and the lower shell are welded to the casing to form a closed space together with the casing.

A discharge pipe 116 is installed above the upper shell 112. The discharge pipe 116 corresponds to a passage through which the compressed refrigerant is discharged to the outside, and an oil separator (not shown) for separating oil mixed in the discharged refrigerant may be connected to the discharge pipe 116. In addition, a suction pipe 118 is installed on the side of the casing 110. The suction pipe 118 is a passage through which the refrigerant to be compressed flows. In FIG. 3, the suction pipe 118 is located at the interface between the casing 110 and the upper shell 112, but the position may be arbitrarily set. In addition, the lower shell 114 also functions as an oil chamber for storing oil supplied so that the compressor can operate smoothly.

The motor 120 as a drive unit is installed at an approximately center portion inside the casing 110. The motor 120 includes a stator 122 fixed to an inner surface of the casing 110 and a rotor 124 positioned inside the stator 122 and rotated by interaction with the stator 122. do. The rotating shaft 126 is coupled to the center of the rotor 124 to rotate together with the rotor 124.

An oil passage 126a is formed in the center of the rotating shaft 126 so as to extend along the longitudinal direction of the rotating shaft 126, and an oil stored in the lower shell 114 is upwardly disposed at a lower end of the rotating shaft 126. An oil pump 126b for supplying is installed. The oil pump 126b may be in the form of a spiral groove in the oil passage or a separate impeller may be installed, or a separate volume pump may be installed.

The upper end of the rotating shaft 126 is formed with an enlarged diameter portion 126c inserted into the boss portion formed in the fixed scroll, which will be described later. The enlarged diameter portion is formed to have a larger diameter than other portions, and a fin portion 126d is formed at an end portion of the enlarged diameter portion. An eccentric bearing 128 is fitted to the pin portion 126d. Referring to FIG. 4, the eccentric bearing 128 is eccentrically fitted with respect to the pin portion 126d and an eccentric bearing 128 with respect to the pin portion 126d. The combination of both is formed to have a substantially "D" shape so that) does not rotate.

The fixed scroll 130 is mounted at the boundary between the casing 110 and the upper shell 112. The fixed scroll 130 has its outer circumferential surface press-fitted between the casing 110 and the upper shell 112 in a shrink fit manner, or may be joined by welding together with the casing 110 and the upper shell 112. have.

On the bottom of the fixed scroll 130, a boss portion 132 into which the above-described rotation shaft 126 is inserted is formed. An upper side of the boss 132 (see FIG. 3) is formed with a through hole through which the pin 126d of the rotation shaft 126 penetrates, thereby allowing the pin 126d of the fixed scroll 130. It is projected to the upper side of the hard plate portion 134.

The upper surface of the hard plate portion 134 is formed with a fixed wrap 136 is engaged with the rotary wrap to be described later to form a compression chamber, the outer peripheral portion of the hard plate portion 134 to accommodate the swing scroll 140 to be described later A side wall portion 138 is formed to form a space portion and contact the inner circumferential surface of the casing 110. A turning scroll support portion 138a is formed inside the upper end of the side wall portion 138 so that the outer circumference of the turning scroll 140 is seated, and the height of the turning scroll support portion 138a is the same as that of the fixed wrap 136. It is formed to have a height slightly smaller than the fixed wrap so that the end of the swing wrap can contact the surface of the hard plate portion of the fixed scroll.

Revolving scroll 140 is installed on the top of the fixed scroll (130). The orbiting scroll 140 has a hard plate portion 142 having a large circular shape and a orbiting wrap 144 to be engaged with the fixed wrap 136 is formed. In addition, an approximately circular rotary shaft coupling part 146 is formed at the center of the hard plate part 142 to which the eccentric bearing 128 is rotatably inserted and fixed. The outer circumferential portion of the rotating shaft coupling portion 146 is connected to the turning wrap to form a compression chamber together with the fixed wrap in the compression process. This will be described later.

On the other hand, the eccentric bearing 128 is inserted into the rotary shaft coupling portion 146 so that the end of the rotary shaft 126 is inserted through the hard plate portion of the fixed scroll, the swivel wrap, fixed wrap and eccentric bearing 128 Is installed to overlap in the radial direction of the compressor. During compression, the repelling force of the refrigerant is applied to the fixed wrap and the swing wrap, and a compression force is applied between the rotating shaft support and the eccentric bearing as a reaction force. As described above, when a part of the shaft penetrates through the hard plate part and overlaps with the wrap in the radial direction, the repulsive force and the compressive force of the refrigerant are applied to the same side with respect to the hard plate so that they cancel each other out. For this reason, the inclination of the turning scroll due to the action of the compressive force and the repulsive force can be prevented.

Although not shown, a discharge hole is formed in the hard plate part 142 to allow the compressed refrigerant to be discharged into the casing. The position of the discharge hole may be arbitrarily set in consideration of the required discharge pressure.

On the other hand, the upper frame 170 is installed on the upper portion of the swing scroll 140, the center of the upper frame 170 is in communication with the discharge hole of the swing scroll 140 to discharge the compressed refrigerant to the upper shell side. A hole is formed.

In addition, a lower frame 160 is installed below the casing 110 to rotatably support the lower side of the rotating shaft 126.

FIG. 6 is a plan view showing a compression chamber immediately after suction and a compression chamber immediately before discharge in a scroll compressor having a swing wrap and a fixed wrap formed of an involute curve, with a portion of the shaft penetrating a hard plate. (A) of FIG. 6 shows the change of the 1st compression chamber formed between the inner side of a fixed wrap and the outer side of a turning wrap, and (b) shows between the inner side of a turning wrap and the outer side of a fixed wrap. The change of the 2nd compression chamber formed is shown.

In the scroll compressor, the compression chamber is formed between two contact points formed by the contact between the fixed wrap and the swing wrap. When the fixed wrap and the swing wrap have an involute curve, two compression chambers are defined as shown in FIG. Contact points are located on a straight line. In other words, the compression chamber is disposed over 360 ° with respect to the center of the rotation axis.

Looking at the volume change of the first compression chamber in Figure 6 (a), the compression chamber immediately after the suction is located in the outer side is gradually reduced in volume while moving to the center by the swinging movement of the turning scroll, the center of the turning scroll It has a minimum value when reaching the outer periphery of the rotating shaft engaging portion located at. In the case of the fixed lap and the swivel lap of the involute curve, the volume reduction rate decreases linearly as the rotation angle of the rotating shaft increases, so to obtain a high compression ratio, the compression chamber should be moved as close to the center as possible. If there is a rotating shaft in the center, it is possible to move the compression chamber only to the outer peripheral portion of the rotating shaft. As a result, the compression ratio is lowered. In FIG. 4A, the compression ratio is about 2.13.

On the other hand, the second compression chamber shown in (b) of Figure 6 has a lower compression ratio than the first compression chamber has a value of approximately 1.46. However, in the case of the second compression chamber, the shape of the turning scroll is changed, and as shown in FIG. 7 (a), the connecting portion between the rotating shaft engaging portion P and the turning wrap has an arc shape. The compression path of the second compression chamber is long, so that the compression ratio can be increased to about 3.0. In this case, the second compression chamber has a range of less than 360 degrees immediately before discharge. However, this method is not applicable to the first compression chamber.

Therefore, in the case of the involute-shaped fixed wrap and the swiveling wrap, the intended compression ratio can be obtained in the case of the second compression chamber, but not possible in the first compression chamber. If there is a difference in the compressor will adversely affect the operation of the compressor.

In order to solve this problem, the fixed wrap and the swing wrap may be formed to have a curve other than the involute curve. 8 and 9, when the center of the rotation shaft coupling portion 146 is referred to as O and the two contact points are P1 and P2, respectively, the centers of the two contact points P1 and P2 and the rotation shaft coupling portion are as follows. It can be seen that the angle α defined by the two straight lines connecting (O) is smaller than 360 °, and the distance l between the normal vectors at each contact point also has a value larger than zero. This increases the compression ratio since the first compression chamber immediately before the discharge has a smaller volume than the case where the fixed wrap and the swirl wrap made up of the involute curves. In addition, the turning wrap and the fixed wrap shown in FIG. 8 have a shape in which a plurality of circular arcs having different diameters and origins are connected, and the outermost curve has a substantially elliptical shape having a long axis and a short axis.

In addition, a protruding portion 137 protruding toward the rotation shaft coupling portion 146 is formed near the inner end of the fixing wrap, and the protruding portion 137 is further provided with a contact portion 137a protruding from the protruding portion. That is, the inner end of the fixing wrap is formed to have a larger thickness than other parts. For this reason, since the wrap strength of the inner end part which receives the largest compressive force among the fixed wraps can be improved, durability can be improved.

Meanwhile, as shown in FIG. 9, the thickness of the fixed wrap gradually decreases, starting with the contact point P1 located inside of the two contact points forming the first compression chamber as shown in FIG. 9. Specifically, the first reduction portion 137b adjacent to the contact point P1 and the second reduction portion 137c connected to the first reduction portion are formed, and the thickness reduction rate at the first reduction portion is the second reduction portion. Is larger than After the second reduction part, the fixing wrap increases in thickness for a predetermined period.

And, when the distance between the inner surface of the fixed wrap and the axis of rotation (O ') of the axis of rotation is D _F , the D _F increases and decreases from the P1 in the counterclockwise direction (see FIG. 9). The interval is shown in FIG. FIG. 10 is a plan view showing the position of the turning wrap 150 ° before the start of discharge. When the rotary shaft is further rotated by 150 ° from the state of FIG. 10, the state shown in FIG. 6 is reached. Referring to FIG. 10, the contact point is located above the rotation shaft coupling part 146. In the section between P1 in FIG. 8 and P1 in FIG. 10, the D _F increases and decreases.

The rotary shaft coupling portion 146 is formed with a recess 145 to be engaged with the protrusion. One side wall of the recess 145 is in contact with the contact portion 137a of the protrusion 137 to form one contact point of the first compression chamber. When the distance between the center of the rotational shaft coupling portion 146 and the outer peripheral portion of the rotational shaft coupling portion 146 is D _o , the D _o decreases after increasing in the interval between P 1 of FIG. 8 and P 1 of FIG. 10. Done. Similarly, the thickness of the rotation shaft coupling portion 146 also increases and decreases in the interval between P1 of FIG. 8 and P1 of FIG. 8.

One side wall of the concave portion 145 is connected to the first increasing portion 145a145b having a relatively rapid increase in thickness, and has a second increasing portion 145b having a relatively low thickness increase. This corresponds to the first reduction portion and the second reduction portion of the fixed wrap, as a result of bending the envelope to the rotational shaft engaging portion, the first increasing portion, the first reducing portion, the second increasing portion and the second reducing portion. As a result, the inner contact point P1 forming the first compression chamber is located in the first increasing portion and the second increasing portion, and the length of the first compression chamber immediately before discharge is shortened, resulting in a compression ratio. To increase.

The other side wall of the recess 145 is formed to have an arc shape. The diameter of the arc is determined by the wrap thickness of the fixed wrap end and the turning radius of the swing wrap, and increasing the thickness of the fixed wrap end increases the diameter of the arc. For this reason, the thickness of the turning wrap of the circular arc may also be increased to ensure durability, and the compression path may be increased to increase the compression ratio of the second compression chamber.

Here, the central portion of the concave portion 145 forms a part of the second compression chamber. FIG. 11 is a plan view showing the position of the turning wrap when discharge is started in the second compression chamber. In FIG. 11, the second compression chamber is in contact with the arc-shaped side wall of the concave portion. One end of the compression chamber passes through the center of the recess.

On the other hand, the upper wall of the swing scroll 140 is provided with an all-dam ring 150 for preventing the rotation of the swing scroll. The old dam ring 150 has a ring portion 152 having a substantially circular shape fitted to the rear surface of the hard disk portion of the pivoting scroll 140 and a pair of first keys 154 protruding to one side of the ring portion 152. And a second key 156. The first key 154 protrudes longer than the thickness of the outer circumferential side of the hard plate portion 142 of the swing scroll 140, the upper end of the side wall portion 138 of the fixed scroll 130 and the pivot scroll support portion 138a It is inserted into the first key groove 154a formed over (). In addition, the second key 156 is coupled to the second key groove 156a formed in the outer circumferential portion of the hard plate portion 142 of the turning scroll 140, respectively.

Here, the first key groove 154a is formed to have a vertical portion extending in an upward direction and a horizontal portion extending in a left and right direction, and the lower end portion of the first key 154 is always in the pivoting movement of the swing scroll. While retained in the horizontal portion of the first keyway 154a, the radially outer end of the first key 154 is formed to be detachable from the vertical portion of the first keyway 154a. That is, since the coupling between the first key groove 154a and the fixed scroll is made in the vertical direction, the diameter of the fixed scroll can be reduced.

Specifically, a clearance corresponding to a turning radius should be secured between the hard plate portion of the turning scroll and the inner wall of the fixed scroll. If the key of the old dam ring is radially coupled with the fixed scroll, the key groove formed in the fixed scroll must be at least larger than the turning radius to prevent the old dam ring from being separated from the key groove in the turning process. It increases the size of the.

On the other hand, if the key groove extends to the lower portion of the space between the hard disk portion and the swing wrap of the swing scroll as in the above embodiment, it is possible to reduce the size of the fixed scroll while ensuring sufficient length of the key groove.

In addition, the old dam ring in the embodiment is all keys are formed on one side of the ring portion, it is possible to reduce the height in the axial direction of the compression unit compared to the case where the keys are formed on each side.

On the other hand, it is necessary to vary the strength of the old dam ring according to the shape of the shaft-through scroll compressor. That is, in a typical involute compression in which the wrap is formed in the involute curve, the moment in the z-direction is not greatly increased because the ejection opening is formed about the center of the axis of the rotation axis. However, in the case of involute circular compression, the Z direction moment is increased as the discharge port is eccentrically oriented from the axis center of the rotating shaft, so that the load transmitted to the Old Damling is not through the shaft, but the scroll of the general involute compression method. It will increase compared to the compressor. Therefore, in the shaft-through scroll compressor including the involute circular compression, the strength of the Olddam ring should be increased to prevent the Olddam ring from being broken.

In particular, in the so-called Crescendo-type arc compression in which protrusions are formed at the beginning of the lap as in the present embodiment, the moment in the Z direction increases further as the discharge port is more eccentric than in the case of involute arc compression. Accordingly, the load transmitted to the old dam ring also increases. 12 is a graph showing the maximum loads for general involute compression, involute circular compression, and crescendo circular compression.

As shown therein, the maximum load on the Oldham ring in the scroll compressor is about 54N for a typical involute compression of 5.5 hp and about 140N for involute circular compression. . On the other hand, in the case of the crescendo circular compression as in the present embodiment, the discharge port has a larger eccentricity than the involute circular compression, and transmits a maximum load of about 230 N to the Oldhamling. This means that the maximum load is increased about 4 times compared to involute compression and about 40% compared to involute circular compression. Therefore, in the so-called crescendo-shaped arc compression, the old dam ring may not be able to withstand the maximum load and may be broken by the old dam ring manufactured by the existing casting method.

In general, the casting method of the old dam ring is aluminum (eight kinds of ALDC) and Fujimite surface treatment, yielding a yield stress of about 282 MPa. In the case of involute compression or involute circular compression, the maximum load of the Old Daming is about 54N and 140N, respectively. However, in the case of crescendo circular compression, the maximum load received by the Oldham ring is about 230N, so the Oldham ring may not be able to withstand the maximum load.

Therefore, in the present embodiment, the Oldham ring is manufactured through a sintering process to increase the yield stress of the Olddam ring to approximately 300N or more. The old dam ring may be manufactured by sintering stainless steel powder. Since the basic configuration and operation of the old dam ring are the same as the above-described example, description thereof will be omitted.

In this way, as the strength of the Olddam ring is greatly improved, even in the case of Crescendo circular compression, in which the maximum load on the Olddam ring is increased, the Olddam ring can be prevented from being broken and the reliability of the compressor can be improved.

110: casing 122: stator
124: rotor 126: rotation axis
126a: oil path 126c: enlarged diameter part
126d: pin 128: eccentric bearing
130: fixed scroll 132: boss
134: hard plate portion 136: fixed wrap
138 side wall portion 140: turning scroll
142: hard plate 144: turning wrap
146: rotating shaft coupling portion 150: Oldham ring
152: ring portion 154,156: first and second keys
154a, 156a: first and second keyway 160: lower frame
170: upper frame

Claims (5)

A fixed scroll having a fixed wrap;
A turning scroll having an orbiting wrap engaged with the fixed wrap to form first and second compression chambers on outer and inner surfaces thereof, the pivoting scroll being pivotal with respect to the fixed scroll;
A frame configured to support the swing scroll by being installed on the opposite side of the fixed scroll with the swing scroll interposed therebetween;
A rotation shaft having an eccentric portion at one end thereof and coupled to the swing scroll such that the eccentric portion radially overlaps the pivot wrap; And
And a driving unit for driving the rotating shaft.
The rotating scroll is further provided with a rotation preventing member for preventing the rotation of the rotating scroll,
The anti-rotation member is a scroll compressor that is formed to have a yield stress of 300MPa or more. The method of claim 1,
The anti-rotation member is a scroll compressor formed by sintering stainless steel powder. The method of claim 1,
The first compression chamber is formed between two contact points (P1, P2) caused by the inner surface of the fixed wrap and the outer surface of the turning wrap,
When an angle having a larger value among angles formed by two lines connecting the center O of the eccentric portion and the two contact points P1 and P2, respectively, is α,
Scroll compressor at least α <360 ° before the start of discharge. The method of claim 3,
And l = 0 when the distance between the normals at the two contact points (P1, P2) is l. The method of claim 1,
At the center of the rotating scroll is formed a rotating shaft coupling portion to which the eccentric portion is coupled,
And a protrusion is formed on an inner circumferential surface of the inner end of the fixed wrap, and a concave portion is formed on an outer circumferential surface of the rotating shaft coupling portion to form a compression chamber in contact with the protrusion.

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