KR20130031734A - Scroll compressor - Google Patents

Abstract

PURPOSE: A scroll compressor is provided to decrease the loss and abrasion of a compressor by obtaining sufficient volume ratio and Sommerfeld number by downsizing the compressor. CONSTITUTION: A scroll compressor comprises a fixed scroll, a rotary scroll(140), a rotary shaft(126), and a driving unit. The rotary scroll is engaged with a fixing lap; is equipped with a rotating lap for forming first and second compressing chambers by outer and inner surfaces; and rotates about the fixing scroll. The rotary shaft is equipped with an eccentric unit by one end. The eccentric unit is combined in the rotary scroll in order to be overlapped to the rotating lap in the radial direction. By assuming the bearing area between the rotary scroll and rotary shaft as A and the end plat area of the rotary scroll as B, the range of A/B is supposed to be between 0.035 and 0.085. [Reference numerals] (A) Bearing area; (B) End plate area

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 surface 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 reaction force for canceling the repulsive force The applied working points are spaced apart from each other in the axial direction so that the turning scroll is tilted during the operation, 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. However, when the rotary shaft extends to the turning wrap portion, the end of the rotating shaft is positioned at the center of the turning wrap, so that the intended compression ratio can be obtained only by increasing the diameter of the hard plate. As a result, the size of the compressor is increased.

In general, in order for the compressor to be applied to an air conditioner, the ratio of the suction volume and the discharge volume (Vr) must be secured at 2.0 or more, and the Sommerfeld Number (Sf) at which the reliability of the bearing can be estimated is 0.005 or more. Should be secured. However, in the conventional shaft-through scroll compressor, since the bearing between the rotating shaft and the turning scroll penetrates the compression part, it is difficult to secure Vr to 2.0 or more without increasing the size of the compressor. However, when reducing the size of the bearing in order to secure the Vr, the number of Sommerfeld was lowered, there was a problem that the reliability of the bearing is lowered while the solid friction occurs.

It is an object of the present invention to provide a scroll compressor capable of obtaining a sufficient volume ratio and a number of sommerfelds while reducing the overall size of the 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 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 drive unit for driving the rotary shaft, wherein the bearing area between the swing scroll and the rotation shaft is A, and the hard plate area of the swing scroll is B, such that A / B is in the range of 0.035 to 0.085. A scroll compressor is provided.

Here, the first compression chamber is formed between two contact points (P1, P2) formed by the inner surface of the fixed wrap and the outer surface of the swing wrap, the center of the eccentric portion (O) 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.

In the scroll compressor according to the present invention, when the bearing area between the swing scroll and the rotating shaft is A, and the hard plate area of the swing scroll is B, A / B is formed so as to be in the range of 0.035 to 0.085, thereby reducing the overall size of the compressor. It is possible to reduce the friction loss and wear of the compressor by making it possible to obtain a sufficient volume ratio and a number of sommer felts while reducing the size of the compressor.

1 is a cross-sectional view schematically showing the internal structure of one embodiment of a scroll compressor according to the present invention;
2 is a partial cutaway view of the compression unit of the embodiment shown in FIG. 1, FIG.
3 is an exploded perspective view of the compression unit shown in FIG.
4 is a plan view showing first and second compression chambers immediately after suction and just before discharge in a scroll compressor having a swing wrap and a fixed wrap in the form of involute;
5 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;
6 is a plan view showing a turning wrap and a fixed wrap obtained by another envelope;
FIG. 7 is an enlarged plan view of a central portion of FIG. 6;
8 is a plan view showing a state in which the turning wrap in the embodiment shown in Figure 6 in the 150 ° position before the discharge start;
9 is a plan view showing a time point at which discharge is started in the second compression chamber in the embodiment shown in FIG. 6;
10 is a schematic view showing the bearing area and the hard plate area separately in this embodiment,
FIG. 11 is a graph showing the relationship between the ratio of the bearing area divided by the hard plate area, the volume ratio, and the number of Sommerfeldt in the embodiment according to FIG. 10; FIG.

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. 1, 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 is introduced. In FIG. 1, the suction pipe 118 is located at an 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. 3, 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. On the upper side of the boss portion 132 (see FIG. 1), a through hole is formed to allow the pin portion 126d of the rotation shaft 126 to pass therethrough, whereby the pin portion 126d is formed 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.

The upper wall of the swing scroll 140 is provided with an old dam ring 150 for preventing 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, a lower frame 160 for rotatably supporting the lower side of the rotating shaft 126 is installed in the lower portion of the casing 110, the upper portion of the turning scroll and the old dam ring 150 The upper frame 170 for supporting each is installed. In the center of the upper frame 170 is formed a hole in communication with the discharge hole of the swing scroll 140 to discharge the compressed refrigerant to the upper shell side.

FIG. 4 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 the hard plate. Figure 4 (a) shows the change of the first compression chamber formed between the inner surface of the fixed wrap and the outer surface of the swing wrap, (b) is between the inner surface of the swing wrap and the outer surface of the 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. 4. 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 4 (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 rotating scroll, the center of the rotating 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 4 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. 5 (a), when the connecting portion of the rotating shaft coupling part P and the turning wrap is arcuate, 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. 6 and 7, 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. 6 have a form 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. 7, 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. 7. 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. 7). The interval is shown in FIG. 8. FIG. 8 is a plan view showing the position of the turning wrap 150 ° before the start of discharge. When the rotary shaft is further rotated 150 ° from the state of FIG. 8, the state shown in FIG. 6 is reached. Referring to FIG. 8, the contact point is located above the rotation shaft coupling part 146, and the D _F increases and decreases in a section between P1 in FIG. 6 and P1 in FIG. 8.

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. 6 and P 1 of FIG. 8. Done. Similarly, the thickness of the rotating shaft coupling portion 146 also increases and decreases in the section between P1 of FIG. 6 and P1 of FIG. 8.

One side wall of the concave portion 145 is connected to the first increasing portion 145a having a relatively sharp increase in thickness and the second increasing portion 145b having a relatively small increase in thickness. ). This corresponds to the first reduction portion and the second reduction portion of the fixed wrap. These first increasing portions, the first decreasing portions, the second increasing portions, and the second decreasing portions are obtained as a result of bending the envelope to the rotational shaft engaging portion side. 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 the discharge can be shortened, thereby increasing the compression ratio. To be.

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. 9 is a plan view showing the position of the turning wrap when discharge is started in the second compression chamber. In FIG. 9, 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, as described above, in order for the compressor to be applied to the air conditioner, the ratio of the suction volume and the discharge volume (Vr) must be secured to 2.0 or more, and the number of Sommerfelds (Sf) must be secured to 0.005 or more. It is not easy to meet these conditions without increasing the size of the compressor. However, as shown in FIG. 7, when the bearing area between the swing scroll and the rotating shaft is A, and the hard plate area (the area including the bearing area) of the swing scroll is B, A / B is in the range of 0.035 to 0.085. If formed, it can be expected to meet the above conditions.

10 is a schematic view showing the bearing area and the hard plate area in this embodiment, and FIG. 11 is a graph showing the relationship between the bearing area divided by the hard plate area (hereinafter, the area ratio), the volume ratio, and the number of the Sommerfelds. As shown here, the volume ratio has a relationship in which the number of the Sommerfelds is inversely proportional to each other with respect to the area ratio. In other words, increasing the volume ratio at the same area ratio lowers the number of Sommerfeld, while increasing the number of Sommerfeld lowers the volume ratio. Therefore, in order to secure the proper volume ratio and the number of Sommerfeld, it is preferable to secure an appropriate area ratio (A / B) as shown in FIG. In this embodiment, when the area ratio (A / B) is designed to maintain 0.035 to 0.085, the rotating scroll and the rotating shaft while ensuring the proper volume ratio and the number of sommer felts, exhibiting the necessary compressor performance in the air conditioner without increasing the size of the compressor. It can reduce friction loss and wear in

The area ratio according to the present embodiment can be evenly applied to all shaft-through scroll compressors.

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 A: bearing area
B: hardboard area

Claims (11)

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 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.
When the bearing area between the swing scroll and the rotating shaft is A, and the hard plate area of the swing scroll is B,
A / B is a scroll compressor that is formed to be in the range 0.035 ~ 0.085. 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 2,
And l = 0 when the distance between the normals at the two contact points (P1, P2) is l. The method of claim 1,
When the inner contact point of the first compression chamber is P3 at the start of discharging, 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 and then increases. Scroll compressor. 5. The method of claim 4,
The scroll compressor having a maximum thickness of the fixed wrap at P3. The method of claim 1,
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 discharge starts. time,
The D _F is a scroll compressor that increases and then decreases from P3 to P4. The method according to claim 6,
Wherein D _F has a minimum value at P3. The method of claim 1,
When the distance between the center of the eccentric portion and the outer circumferential surface of the turning wrap is D _O ,
When the inner contact point of the first compression chamber is P3 at the start of discharging, and the inner contact point of the first compression chamber is P4 at 150 ° before the start of discharge, the D _O increases and decreases from P3 to P4 and then decreases. . 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. The rotating shaft according to any one of claims 1 to 9,
A shaft portion connected to the driving unit;
A pin portion formed concentrically with the shaft portion at the end of the shaft portion; And
Includes; an eccentric bearing eccentrically fitted to the pin portion,
The eccentric bearing is scroll compressor is rotatably coupled to the rotating shaft coupling portion. The method of claim 10,
And the pin portion is formed to have an asymmetrical shape.

Images