KR20000075314A - scroll type compressor - Google Patents

Abstract

PURPOSE: A scroll compressor is provided to achieve an improved compression efficiency by allowing the scroll wrap to smoothly correspond to a pressure change caused by a refrigerant compression, while removing stress concentration caused at end of scroll wrap by an over-compression of the refrigerant. CONSTITUTION: A scroll compressor comprises a fixed scroll and a swirling scroll. The fixed scroll is fixed to a main body and has a wrap(151) which is protruded, forming a volute curve. The swirling scroll has a wrap which is protruded in correspondence with the wrap of the fixed scroll, and is engaged with the fixed scroll so as to make a revolutionary swirling motion with a predetermined radius vector for the center portion of the fixed scroll. When the radius vector of the volute curve formed by the scroll wraps is function "F(b)", coefficients of the algebraic spiral are "A" and "k", an angle of deviation is "b", and the integer numbers are "i" and "n", the relation satisfies the expression F(b)=QAibki.

Description

Scroll compressor {scroll type compressor}

TECHNICAL FIELD The present invention relates to the field of compressors, and more particularly, to a scroll structure of a scroll compressor in which compression of a refrigerant is performed according to the rotation of the scroll.

In general, scroll compressors are mainly used in room air conditioners or automotive air conditioners because of high efficiency, low noise, compactness, and light weight, and are used to compress gas gas by a pair of scrolls opposed to each other.

Such a scroll compressor includes a suction tube 11 for sucking refrigerant from an evaporator 2 of a cooling cycle and a condenser 3 of a cooling cycle in a sealed container-shaped body 1 as shown in FIG. Discharge pipes 12 for discharging the coolant are respectively provided.

A fixed scroll 13 having a discharge port 13b is fixed to an inner upper side of the main body, and a wrap 13a protrudes from the lower side thereof in an involut shape.

In addition, below the fixed scroll, a rotating scroll 14 having an involute wrap 14a formed on the upper side of the fixed scroll so as to be coupled with the fixed scroll is rotatable.

The sides of the wraps 13a and 14a formed on the fixed scroll 13 and the revolving scroll 14 are connected to each other and at the same time, the front ends of the wraps 13 and 14c overlap with each other. By being installed in a state, a compression chamber (a space gradually reduced in a sealed state so that the introduced refrigerant can compress) is formed.

In addition, the turning scroll is coupled to the crank shaft 15 is to receive the rotational force by the drive of the motor 16 provided in the lower portion in the main body 1 through the crank shaft to turn, Oldham's rings ( 17) the discharge chamber formed in the fixed scroll 13 after compressing the refrigerant gas introduced between the two scrolls 13 and 14 by sequentially changing the compression chamber while performing the pivoting movement in a state where the rotation is prevented by the rotation. The discharge tube 12 is discharged through 13a.

The operation of the conventional scroll compressor configured as described above will be described in more detail.

First, when power is applied to the motor 16, the crankshaft 15 rotates to rotate the turning scroll 14 provided at the upper end thereof.

At this time, the old dam ring 17 disposed between the lower side of the turning scroll 14 and the upper side of the frame constituting the main body 1 prevents the turning force of the turning scroll 14 to rotate by the rotational force of the crankshaft 15. It keeps its shape in one state and rotates it to form a small circle.

In this process, the low temperature and low pressure refrigerant sucked through the suction pipe 11 after heat exchange from the evaporator 2 is provided in the fixed scroll 13 and the turning scroll 14, respectively, as shown in FIG. 2A. After flowing through the inlet of the flow path formed by the involute wraps 13a and 14a, the area of the compression chamber is gradually reduced by continuous turning of the turning scroll 14 as shown in FIG. 2b. Inward, that is, it flows to the position in which the discharge port 13b of the fixed scroll 13 was formed.

As described above, it can be understood that the refrigerant is compressed to high temperature and high pressure by gradual volume reduction as described above, and the compressed refrigerant is eventually discharged through the fixed scroll 1 as shown in FIG. After discharged to the discharge chamber 18 through 13b), it is discharged to the condenser 3 through the discharge tube 12.

In the conventional scroll compressor which performs the above-described action, it is one of the important factors to design the scroll scroll and the fixed scroll so that the respective wraps of the turning scroll and the fixed scroll closely contact each other at the proper position as the refrigerant is gradually compressed toward the compression chamber.

Hereinafter, the involute curve design process of the turning scroll and the fixed scroll of the conventional scroll compressor will be described in detail.

First, as shown in FIG. 3A, a virtual base circle 20 having a radius “a” is formed based on the centers on the X and Y axes.

When the base circle 20 is formed as described above, the involute is started at any point of the periphery of the base circle, that is, at a point around the base circle 20 having an angle of α from the X axis. That is, the first basic curve (Basic-Curve) 21 is formed.

At this time, the angle (involute angle; ψ) that forms the center point of the base circle and the first basic curve 21 is 90- Each point of the first basic curve 21 gradually formed has an angle of X = a {cosψ + (ψ-α) sinψ} and Y = a {sinψ- (ψ-α) cosψ}. Will be achieved.

Further, as shown in FIG. 3B to form the thickness of the wrap 14a of the scroll 14, another involute, i.e., a point having an angle of -α as the starting point, is shown. , The second basic curve 22 is formed.

In other words, if the first involute curve is an inner involute curve, the subsequent involute curve becomes an outer involute curve, and a constant thickness for forming a wrap is formed by the interval between the involute curves.

When the design of the involute is completed as described above, the rotating scroll 14 of the scroll compressor as shown in FIG. 3C is formed using the designed involute curve.

Moreover, the fixed scroll 13 is comprised by the shape which gave the phase difference of 180 degrees with the shape of the said turning scroll like FIG. 4A, 4B, 4C shown.

That is, the foundation circle 30 is formed in the same manner as the foundation circle 20, which was determined as the initial reference point for the formation of the turning scroll 14, and each turning curve 31 is based on one point of the foundation circle. After forming the 32, the fixed scroll 13 of the scroll compressor is formed on the basis of the respective turning curves, and thus a detailed description thereof will be omitted.

At this time, by forming the discharge port 13b to communicate with the discharge pipe 12 at the initial formation point of the wrap 13a constituting the fixed scroll, that is, the bottom surface of the center portion of the fixed scroll, the compressed refrigerant can be discharged. .

In addition, the turning radius 14 of the turning scroll 14 in order to make the appropriate positions of the respective laps 13a and 14a formed on the turning scroll 14 and the fixed scroll 13 configured as described above contact each other. ) Must have a relationship of (P-2t) / 2.

Where P is In this case, it means the pitch of the laps 13a and 14a formed on each scroll, and t means the thickness of the lap as 2aα.

Therefore, the turning scroll 14 is rotated by the driving of the motor 16 ( The compression chamber is formed while turning along), and the refrigerant introduced into the compression chamber is compressed.

However, considering that the current trend is to study the miniaturization of the compressor while maintaining a high efficiency, there is a limit to the formation of the wrap of each scroll according to the above-described design.

That is, in order to increase the capacity of the scroll compressor, the overall size of the scroll compressor or the height of the wrap formed on each scroll was inevitably increased.

However, this not only violates the current trend for miniaturization of the compressor, but if the height of the lap formed on each scroll is increased, the pressure generated by the compression of the refrigerant is the point of action of the increased lap height. This increases the overall moment that the wrap receives, resulting in a decrease in reliability.

Accordingly, a scroll having a shape as shown in US Pat. No. 5,542,512 as shown in FIG. 5 has been developed to simultaneously solve the above-described problems.

Hereinafter, the shape of each of the improved scrolls and the method of forming the same will be described in detail below.

First, the shapes of the scrolls 50 and 60 constituting the scroll compressor of the improved form are wraps formed on the scrolls from the side into which the refrigerant flows into the compression chamber from the side through which the refrigerant flows out through the discharge port 52. It is formed by an algebraic spiral so that the thickness of the (51) (61) gradually becomes thick.

This is a form to increase the refrigerant inlet volume of the compression chamber as a whole, even if the scroll compressor of the same size as the conventional it is possible to further increase the amount of the refrigerant introduced and the amount of the refrigerant to compress.

That is, as the thicknesses of the wraps 51 and 61 formed on the scrolls 50 and 60 become thinner toward the refrigerant inflow side, the volume of the refrigerant flowing into the refrigerant increases as the thickness of the wrap decreases. As it is introduced through the inflow side, compression is performed in the compression chamber.

Each of the scrolls 50 and 60 having such a shape is formed in a different form from the conventional method of forming the scrolls 13 and 14.

If the thickness of the wrap is increased from the refrigerant inlet side to the refrigerant discharge side as described above in the state in which each scroll is designed in the same manner as in the prior art, each wrap formed in the turning scroll and the fixed scroll according to the turning scroll This is because the contact points between the two are different or smooth contact is not made.

Hereinafter, as described above, a design method in which the thickness of the lap increases from the refrigerant inlet side to the refrigerant discharge side is increased, but the contact between the laps according to the turning of the turning scroll can be smoothly described as follows.

First, as shown in FIG. 6A, a first basic-volute curve 71 is formed with the center on the X and Y axes as a starting point.

At this time, the turning radius of the first basic turning curve is In the end, the first fundamental pivot curve is Phosphorus (r, It is formed by the polar coordinate of).

In the above, a means a general coefficient, Is an angle of deviation, and k is an exponent value for forming an algebraic vortex.

That is, the deflection angle ( In the process of gradually changing), a predetermined first basic turning curve 71 is formed by substituting a predetermined k value.

When the first basic turning curve 71 is formed as described above, as shown in FIG. 6B, from the Y axis based on the first basic turning curve as shown in FIG. 6B. A first turning curve 72 having a turning radius equal to the first basic turning curve is formed using the point of the starting point, and from the Y axis The second turning curve 73 having the same turning radius as the first basic turning curve is formed using the point of the starting point.

At this time, Value and The values may be the same or different from each other, so that they can be set differently depending on the needs of the user or the structure of the cooling cycle.

Also, apart from the first basic turning curve 71 formed as described above, a second basic having a phase difference of 180 ° with respect to the first basic turning curve, starting from the center on the X axis and the Y axis, as shown in FIG. 6C. The turning curve 81 is formed.

At this time, the turning radius r of the second basic turning curve is also the same as the turning diameter of the first basic turning curve 71.

When the second basic turning curve 81 is formed as described above, the second basic turning curve 81 is formed from the Y axis based on the second basic turning curve as shown in FIG. 6D. A third spiral curve 82 having the same turning radius as the second basic pivot curve is formed using the point at which is the starting point. As a starting point, a fourth turning curve 83 having the same turning radius as the second basic turning curve is formed.

Even at this time, Value and It is understood that the values may be identical to one another, may be different from each other, and the value may be zero.

As described above, when the first twist curve 72, the second twist curve 73, the third twist curve 82, and the fourth twist curve 83 are formed, the respective twist curves are fixed in combination with each other. The wraps 51 and 61 of the scroll 50 and the revolving scroll 60 are formed.

That is, on the basis of one scroll formed by combining the first turning curve 72 and the third turning curve 82 with each other, a wrap 61 of the turning scroll 60 as shown in FIG. 6E is formed and the second turning is made. The wrap 51 of the fixed scroll 50 as shown in FIG. 6F is formed on the basis of another scroll formed by combining the curve 73 and the fourth swirl curve 83 with each other.

At this time, the ends of each wrap formed as described above do not form an accurate curve.

This is due to an error that occurs during the process of combining the starting points of the respective turning curves, so that the parts forming this error can be properly formed through machining.

Such processing is based on the center of the X-axis and Y-axis as shown in Figure 6g for the wrap formed on the turning scroll or Having a value Half of the value, The point located on the -X axis by / 2 is the center point After forming a base circle having a value as its radius, the machining is performed using a separate processing tool along the circumference of the base circle as shown in FIG. 7A.

In addition, in the case of the wrap formed on the fixed scroll, the center of the X axis and the Y axis as shown in 6h is shown. or Having a value Half of the value, The point located on the + X axis by / 2 is the center point After forming a base circle having a value as its radius, the machining is performed using a separate processing tool along the circumference of the base circle as shown in FIG.

At this time, the processing of each of the wraps, first, the first processing is performed along the inner curve of the inner end of the wrap as a starting point, and then again the machining along the outer curve of the inner end of the wrap as a starting point By doing so, it is possible to achieve a smooth close contact between the wraps.

Each of the scroll scrolls 60 formed as described above has its turning radius set so as to be able to pivot along the circumference of the base circle virtually formed to form the wrap of the fixed scroll.

That is, the orbiting radius of the turning scroll is or To be.

This is to enable continuous close contact by turning the wrap 61 end of the turning scroll along the inner end of the wrap end of the fixed scroll and to obtain an increase in compression efficiency accordingly.

Therefore, performing the cooling cycle, first, the refrigerant flows in between the lap scrolls 51 and 61 formed in the fixed scroll 50 and the swing scroll 60 through the refrigerant inflow side of the scroll compressor, as shown in FIG. 8A, In this state, the compression chamber is formed by the continuous turning of the turning scroll, and the refrigerant is gradually compressed as shown in FIGS. 8B and 8C, and flows to the refrigerant outlet side, that is, the discharge port 52. It is discharged to the condenser 3 through the discharge port, and the refrigerant is reflowed through the refrigerant inlet side as shown in FIG. 8D.

At this time, the amount of the refrigerant flowing into the refrigerant inlet can be introduced in a larger amount than the amount of refrigerant flowing into the refrigerant inlet when using the fixed scroll 13 and the turning scroll 14 of the conventional general shape. As a result, the compression efficiency could be increased.

However, while the conventional scroll compressor as described above has the advantages as described above, there are also various problems as described below.

First, as described above, the scroll compressor has a nonlinear inflow of the refrigerant flowing into the compression chamber of each scroll and a nonlinear compression thereof, while the wraps of the scrolls have a linear relationship. As a result, there is a problem that the compression of the refrigerant is not made smoothly.

This is because each wrap formed on each scroll is curved and the shape of the compression chamber formed by the contact between the wraps is also non-linear, so the compression of the refrigerant in the compression chamber is only non-linear. In addition, the pressure due to the compression of the refrigerant also occurs non-linearly.

However, in the conventional scroll compressor as described above, as the thickness of the lap formed on each scroll is formed to increase or decrease only linearly, continuous contact between the laps is impossible, and thus, the pressure change due to the compression of the refrigerant You will not be able to respond appropriately.

That is, the wrap of each scroll The value of the exponent (k) in the above equation is a deflection angle when formed to form a turning curve based on the equation of. It is understood that the above-described problems occur because they are always constant regardless of the change in.

Second, in the construction of the improved scroll compressor as described above, in order to form such that the ends of the wraps constituting each scroll can always be in contact with each other, it is necessary to process a fine wrap.

That is, as the inner thickness of the lap and the outer curve of the lap are respectively processed to accurately set the thickness of the lap, the productivity is reduced due to the long manufacturing time.

Third, the refrigerant discharge side in which the refrigerant is discharged in the compression chamber formed by the close contact between the laps formed on the scrolls generally becomes the point where the pressure received by each lap is increased as the refrigerant is compressed.

Nevertheless, conventionally, as the ends of the wraps formed on the scrolls are in contact with each other until all the discharge of the refrigerant is completed, not only stress concentration occurs at the ends of the wraps, but also overcompression occurs. There is a problem that is made.

That is, because the discharge port formed in the center of the fixed scroll is formed by a certain radius while the end of the wrap is in continuous contact with the contact continuously during the rotation period of the revolving scroll, the concentration of stress at the end of the wrap This will cause breakage of the wrap as well as overcompression.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems, and the purpose of the present invention is to allow each wrap formed on each scroll to respond smoothly to pressure changes due to the compression of nonlinear refrigerant in the compression chamber formed in the scroll compressor. There is this.

Another object of the present invention is to prevent the overcompression of the refrigerant generated at the end of each wrap, and also to prevent the stress concentration phenomenon accordingly.

1 is a longitudinal sectional view showing a general scroll compressor;

Figure 2a is a configuration diagram showing the initial state that the refrigerant is introduced into the compression chamber during the operation of a typical scroll compressor

FIG. 2B is a configuration diagram showing a state in which the turning scroll shown in FIG. 2A is rotated 90 degrees.

FIG. 2C is a block diagram showing a state in which the turning scroll of FIG. 2A is rotated 180 degrees. FIG.

FIG. 2D is a block diagram showing a state in which the turning scroll of FIG. 2A is turned 270 °.

Figure 3a, 3b, 3c is a state diagram showing the process of forming a wrap constituting the swing scroll of a typical scroll compressor

Figure 4a, 4b, 4c is a state diagram showing the process of forming a wrap constituting a fixed scroll of a typical scroll compressor

5 is a longitudinal sectional view of an improved scroll compressor.

6A, 6B, 6C, 6D, 6E, and 6F are state diagrams illustrating a process of forming a wrap constituting each scroll of the improved scroll compressor.

Figure 7a is a state diagram showing the processing of the wrap formed on the swing scroll of the improved scroll compressor

Figure 7b is a state diagram showing the processing of the wrap formed on the fixed scroll of the improved scroll compressor

Figure 8a is a block diagram showing the initial state that the refrigerant flows into the compression chamber during the operation of the improved scroll compressor

FIG. 8B is a configuration diagram showing a state in which the turning scroll shown in FIG. 8A is rotated 90 degrees.

FIG. 8C is a configuration diagram showing a state in which the turning scroll of FIG. 8A is rotated 180 degrees. FIG.

FIG. 8D is a configuration diagram showing a state in which the turning scroll of FIG. 8A is turned 270 °.

9A, 9B, 9C, 9D, 9E, and 9F are state diagrams illustrating a process of forming a wrap constituting each scroll of the scroll compressor according to the present invention.

Figure 10a is a state diagram showing the process of processing to form a wrap of the rotating scroll of each scroll of the scroll compressor according to the present invention

Figure 10b is a state diagram showing the process of processing to form a wrap of the fixed scroll of each scroll of the scroll compressor according to the present invention

11A is a configuration diagram showing an initial state in which refrigerant is introduced into a compression chamber during the operation of an improved scroll compressor;

11B is a configuration diagram showing a state in which the turning scroll shown in FIG. 11A is rotated 90 degrees.

FIG. 11C is a configuration diagram showing a state in which the turning scroll of FIG. 11A is rotated 180 degrees. FIG.

FIG. 11D is a configuration diagram showing a state in which the turning scroll of FIG. 11A is turned 270 °.

Explanation of symbols for main parts of the drawings

150. Fixed scroll 151. Fixed scroll wrap

152. Outlet port 153. Arc part of fixed scroll

160. Slewing Scroll 161. Slewing Scroll Wrap

163. Arc part of turning scroll 171. First turning curve

172. Second Curve Curve 181. Third Curve Curve

182. Fourth Curve Curve 191. Involute Surface

According to the aspect of the present invention for achieving the above object, the fixed scroll is fixed in the main body and the protrusion is formed while forming a vortex curve (volute curve) and a separate wrap corresponding to the wrap formed on the fixed scroll The rotating scroll is provided with a rotating scroll having a predetermined turning radius with respect to the center of the fixed scroll in a state where the lap is protruded, wherein the radial vector of the turning curve formed by the wrap of each scroll is Function “F ( ) ”, The F ( ) Is the coefficient of the algebraic spiral, ”,“ ”And the angle of deviation“ ”And an integer number“ ”,“ And mutually There is provided a scroll compressor characterized by having a relationship of.

Hereinafter, with reference to Figures 9a to 12 attached to an embodiment of the present invention in more detail as follows.

9A, 9B, 9C, 9D, 9E, and 9F are state diagrams illustrating a process of forming a wrap constituting each scroll of the scroll compressor according to the present invention, and FIG. 10A is a turning of each scroll of the scroll compressor according to the present invention. Figure 10b is a state diagram showing a process of processing to form a wrap of the scroll, Figure 10b is a state diagram showing a process of processing to form a wrap of the fixed scroll of each scroll of the scroll compressor according to the present invention.

11A is a block diagram showing an initial state in which refrigerant flows into the compression chamber during the operation of the improved scroll compressor, and FIG. 11B is a block diagram showing a 90 ° turning of the turning scroll of FIG. 11A, and FIG. 11A is a configuration diagram showing a state in which the turning scroll rotates 180 °, and FIG. 11D is a configuration diagram showing a state in which the turning scroll of FIG. 11A turns 270 °. ) Is the coefficient of the algebraic spiral, ”,“ ”And the angle of deviation“ ”And an integer number“ ”,“ "about The angle of deflection so that Pitch intervals of the wraps 151 and 161 and the thickness of the wraps 151 and 161 according to It depends on the value of ”.

The process of forming the wrap 151, 161 of the fixed scroll 150 and the revolving scroll 160 according to the present invention using the above relationship will be described in more detail.

First, as shown in FIG. 9A, the deflection angle (based on the virtual X and Y axes) ), So that the pitch spacing can be nonlinearly widened or narrowed Function F with relation ) Virtually forms the first turning curve composed of the turning mirror.

That is, the deflection angle The first spiral curve 171 is gradually formed to narrow or widen the pitch between the curves in accordance with the change of.

In the above relation of the turning curve of the wrap 151, 161 formed on each scroll The value is related to the pitch of the swirl curve forming the lap As the value is large and small, the longitude of the turning curve increases or decreases.

Also, The value of is related to the scroll size and the compression capacity of the overall scroll compressor. If the value is increased, a larger capacity scroll compressor can be formed, and if the value is smaller, a smaller scroll compressor can be formed. .

This can be appropriately adjusted according to the needs of the user, so that the numerical limitation is not.

As a result, it is understood that the turning curve formed by each of the above relationships can achieve a non-linearly changing curve.

At this time, the reason why the turning diameter of the wrap 151, 161 formed on each scroll is changed non-linearly is that the wrap 161 formed on the turning scroll 160 is rotated according to the turning scroll as described above. This is to allow accurate compression of the refrigerant by allowing the contact with the wrap 151 of the fixed scroll 150 to be continuously made in the turning process.

When the first virtual spiral curve 171 is formed by the above process, as shown in FIG. Position as the starting point F ( An imaginary second spiral curve 172 having a function of

At this time, the F ( As described above, the second virtual spiral curve 172 having a function of Subject to the above relationship, in which case Instead of in an expression You only need to substitute it.

In addition, as shown in FIG. 9C, the F ( ) And F (to have a phase difference of 180 ° An imaginary third curve 181 having a function of

When the virtual third curve 181 is formed as described above, as shown in FIG. 9D, the starting point of the third curve is X-axis. Position as the starting point F ( An imaginary fourth spiral curve 182 having a function of

When the virtual first spiral curve 171, the second spiral curve 172, the third spiral curve 181, and the fourth spiral curve 182 are formed as described above, the respective spiral curves are combined to rotate. The wrap 161 of the scroll 160 is formed and the wrap 151 of the fixed scroll 150 is formed at the same time.

In other words, as shown in FIG. 9E, the lap 161 of the turning scroll 160 is formed by combining the first turning curve 171 and the fourth turning curve 182. The spiral curve 172 and the third spiral curve 181 are combined to form the wrap 151 of the fixed scroll 150.

At this time, the first turning curve 171 becomes the inner surface of the wrap 161 formed on the turning scroll 160, the fourth turning curve 182 is the outer side of the wrap 161 formed on the turning scroll 160 The curved surface, the second curve 172 is the inner surface of the wrap 151 formed on the fixed scroll 150, the third curve 181 is the outer surface of the wrap 151 formed on the fixed scroll 150 It becomes a surface.

In addition, an involute curved surface 191 having an imaginary base circle radius is formed at the inner ends of the inner curved surfaces 171 and 172 forming the wrap of each scroll.

The inner ends of the wraps 151 and 161 forming the involute curved surface 191 as described above are formed with arc portions 153 and 163 having arc shapes, respectively, to form the inside of each wrap. The curved surfaces 171, 172 and the outer curved surfaces 181, 182 are interconnected to allow each wrap 151, 161 to achieve a constant thickness.

The reason why the arc portions 153 and 163 are formed at the inner ends of the respective wraps is that the wraps 151 and 161 of each scroll are always provided at a constant interval ( ) So as to be spaced apart from each other, so that the refrigerant reaches the inner end of each wrap to prevent overcompression occurring in the process of being discharged through the discharge port 152 of the fixed scroll 150. As a result of solving the concentration of stress at the inner end of each of the wraps 151 and 161 by the same overcompression, the more stable refrigerant compression is performed by preventing the overcompression and eliminating the stress concentration as described above. Being able to be understandable.

At this time, the interval (between the arc portion 153, 163 of the wrap 151, 161 formed on each scroll ( ) Is less than or equal to the thickness of the wrap, so that even if the turning scroll 160 turns, the wrap 151 formed on the fixed scroll 150 is an arc portion 163, which is an end of the wrap 161 formed on the turning scroll. It is preferable not to contact the arc portion 153, which is the end of the).

Also, at this time, ) Should not be formed, because the excessive space as described above can be discharged without a smooth compression of the refrigerant.

The virtual turning curve start part for forming each lap is not necessarily a curve of the involute shape, but the involute as described above for the convenience of processing and smoother turning scroll can be achieved. It is most preferable to form a curve so as to prevent the interference phenomenon that may occur between the laps according to the turning of the turning scroll.

On the other hand, the formation of each of the wrap 151, 161 as described above to achieve the exact shape by performing the machining, will be described in more detail with reference to Figure 10a, 10b showing such a machining process. It is as mentioned later.

First, the process of processing each wrap is performed using a separate processing tool 200 and the like.

That is, using a separate processing tool is to be processed to a predetermined thickness (t) from the inner or outer end of the inner curved surface of each wrap (151, 161).

At this time, the constant thickness is a value that can be different according to the user's needs. When a large amount of refrigerant compression is required, the t value is set to be large, and the processing is performed. If necessary, it simply sets the value of t so that the inner curvature of each wrap can achieve the correct radius of curvature, and the machining is performed.

In this case, unlike the prior art, only the inner curved surface of each wrap 151 or 161 is processed.

As the inner curved surface and the outer curved surface of each conventional wrap are formed in a linear relationship as a whole, the rotating scroll wrap 60 and the fixed scroll 50 wrap 51 by the turning scroll 60. In order to ensure continuous contact at all times, only one side cannot be processed, and the inner and outer surfaces must be simultaneously processed.

However, in the present invention, since the inner curved surface and the outer curved surface of each wrap are formed in a non-linear relationship, even if only the inner curved surface of each wrap is processed, each wrap 151 (161) according to the turning of the turning scroll 160 This is because continuous contact between the two can be made smoothly.

In addition, as described above, the formation of the involute curved surface 191, which forms the inner end of each wrap 151, 161, is also possible by using the processing tool 200 or the like. This can be done by removing the involute curved surface 191. Set angle based on the imaginary base circle with Only the curved surface will be formed.

The set radius forming the basic circle in the above ( ) And the set angle of the involute surface ) Is a value that can vary depending on the size of each wrap, so do not limit to this.

As a result, as described above, the wrap scrolls 151 and 161 of the fixed scroll 150 and the revolving scroll 150 are respectively formed, and the action of the scroll compressor formed by combining the scrolls with each other is described above. The same structure as that of the conventional scroll compressor is improved, but the structure formed between the ends of each wrap maintains a proper interval at all times as shown in FIGS. 11A to 11D.

At this time, the detailed description of the operation of the scroll compressor according to the present invention will be omitted as it is made the same as the operation of the conventional scroll compressor as described above.

As described above, the scroll compressor according to the present invention can obtain various effects as described below.

First, the present invention has the effect that it is possible to smoothly cope with the pressure change due to the compression of the refrigerant non-linearly in the compression chamber as each wrap has a non-linear curved surface according to the deflection angle.

That is, the shape of the wrap It is possible to appropriately cope with the compressive force of the refrigerant to be nonlinearly compressed by being formed nonlinearly, which is a state based on the equation of.

Second, even if the scroll compressor is the same size can be designed to obtain a different range of compression efficiency, there is an effect that can be properly applied to various cooling systems.

This means that although the pitch of the lap formed on each scroll varies with a certain relationship, the change can be made non-linearly, and the thickness of the lap can also be changed non-linearly. This is because the configuration can be made smoothly.

That is, in the prior art, the thickness of each part of the lap was always only linear, but in the present invention, the thickness according to each part of the lap is designated as a function value so as to have a non-linear relationship. Changes can be made.

Third, the present invention is configured to maintain a constant interval between the ends of the wrap formed on each scroll at all times to prevent the overcompression of the refrigerant generated at the end of each wrap as well as stress concentration phenomenon accordingly There is also an effect that can be prevented.

That is, in the related art, the end of each lap is continuously compressed by the turning of the turning scroll, so that the refrigerant is compressed, thereby achieving an overcompression state in which the refrigerant is continuously compressed during the discharge of the refrigerant. In the present invention, the interval between the wraps in the process of discharging the refrigerant ( ), No further compression is performed, and eventually, overcompression can be prevented.

Fourth, the present invention has an effect that the manufacturing time is shortened as the processing of each wrap is simply performed.

That is, in the prior art, the shape of the lap required by processing the inner surface and the outer surface of the lap at the same time achieved the shape of the lap required by processing only the inner surface of the lap, the manufacturing time can be achieved This can be antagonized.

Claims (4)

The fixed scroll, which is fixed in the main body and has a wrap formed with a volute curve, protrudes from the fixed scroll, and a separate wrap protrudes corresponding to the wrap formed on the fixed scroll, and is engaged with the fixed scroll. In having the turning scroll which turns while having a constant turning longitude with respect to the center part, The radial vector of the spiral curve formed by the lap of each scroll is a function “F ( ) ”, The F ( ) Represents the coefficient of the algebraic spiral “A”, “k” and the angle of deviation “ And “i” and “n” are integer numbers. Scroll compressor, characterized in that having a relationship. The method of claim 1, F ( Form an imaginary first curve of curve to have a function of), and start from the starting point of the first curve of curve to the X axis. Position as the starting point F ( And forming a virtual second spiral curve to have a function of ) And F (with 180 ° phase difference) Form an imaginary third curve to have a function of), and from the starting point of the third curve Position as the starting point F ( A virtual fourth spiral curve is formed so as to have a function of?, And the virtual first spiral curve and the fourth spiral curve are combined to form a wrap scroll, and the virtual second spiral curve and the third spiral curve Scroll compressor characterized in that to form a wrap of the fixed scroll in combination. The method of claim 2, The starting portion of each of the imaginary vortex curves forming the lap of each scroll, which is an inner portion of the first and third vortex curves, is formed to have an involute curve having an imaginary base circle radius. A scroll compressor, characterized in that an arc-shaped arc is formed at the curved end of the involute shape so that the wraps of each scroll are separated from each other at regular intervals. The method of claim 3, wherein And the spacing between the laps of each scroll is less than or equal to the thickness of the laps.