JP6956127B2 - Scroll compressor - Google Patents

Description

The present invention relates to a scroll type compressor that compresses a fluid in a compression chamber partitioned by a fixed scroll and a swirl scroll.

The scroll type compressor has a fixed scroll fixed in a housing and a swivel scroll that revolves with respect to the fixed scroll. The fixed scroll has a fixed side substrate and a fixed side spiral wall erected from the fixed side substrate, and the swivel scroll has a swirl side substrate and a swirl side swirl wall erected from the swivel side substrate. .. Then, the fixed-side spiral wall and the swirl-side spiral wall are meshed with each other, so that the compression chamber for compressing the refrigerant (fluid) by reducing the volume based on the revolution motion of the swirl scroll is partitioned.

In such a scroll type compressor, the fixed side spiral wall and the swirl side spiral wall are often formed by using an involute curve. For example, in the scroll type compressor disclosed in Patent Document 1, one circumference of the fixed side spiral wall and the swirl side spiral wall is formed based on the involute curve, and the wall thickness is constant. In addition, the inner peripheral side of the portion formed by the involute curve is formed based on the correction curve, and the wall thickness changes.

In particular, on one end side of the fixed-side spiral wall and the swirl-side spiral wall, a correction coefficient is set so that the distance from the origin of the base circle of the involute curve becomes small, and the correction curve is corrected by the correction coefficient. It is formed based on. Therefore, the wall thickness on the end side forming the high-pressure compression chamber immediately before discharge is increased to improve durability.

Japanese Unexamined Patent Publication No. 07-35058

By the way, in the scroll type compressor, the compressive force fluctuates greatly immediately before the refrigerant is discharged from the high-pressure compression chamber, that is, immediately before the completion of compression, and vibration caused by the fluctuation occurs. In the scroll type compressor of Patent Document 1, the wall thickness of the spiral wall is set so as to withstand the high pressure immediately before the completion of compression, but no countermeasure is taken for the vibration immediately before the completion of compression.

An object of the present invention is to provide a scroll type compressor capable of reducing vibration caused by fluctuations in compressive force.

The scroll type compressor for solving the above problems includes a fixed-side substrate, a fixed scroll having a fixed-side spiral wall erecting from the fixed-side substrate, a swivel-side substrate facing the fixed-side substrate, and a swivel-side substrate. A swirl scroll having a swirl-side swirl wall that stands up from the swivel-side substrate toward the fixed-side board and meshes with the fixed-side swirl wall. In a scroll type compressor that compresses fluid in a compression chamber partitioned by a swirl scroll, the center of the base circle of the involute curve drawn by the fixed side spiral wall and the center of the base circle of the involute curve drawn by the swirl side spiral wall. The distance between the straight line passing through both of the above and the point where the fixed-side spiral wall and the swirl-side swirl wall come into contact with or are close to each other to partition the compression chamber is defined as a partition point distance, and the swivel angle of the swirl scroll is defined as the compression chamber. The swirl angle at which The turning angle that starts contact with a part of the inner peripheral surface that is connected to the tip of the fixed-side spiral wall and draws an arc is defined as the tip contact starting angle, and the relationship between the turning angle and the section point distance is described from the turning start angle. The division point distance is at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning angle in the range from the tip contact start angle to the turning end angle until the turning end angle. The gist is to reach the maximum.

According to this, the volume of the compression chamber on the central side formed by the contact or proximity of the fixed-side spiral wall and the swirl-side spiral wall becomes zero, and the compressive force fluctuates greatly immediately before the completion of compression. However, compression is completed by providing a position where the division point distance is maximized at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning angle in the range from the tip contact start angle to the turning end angle. At the same time as the fluctuation of the previous compression force, the fluctuation of the compression force in another compression chamber can be generated. As a result, the fluctuations in the compressive force can be canceled out between the compression chamber on the central side and the other compression chambers, and the reduction range of the compressive force can be reduced. As a result, sudden fluctuations in compressive force can be suppressed and vibration can be reduced.

Further, for the scroll type compressor, the division point distance may be maximized at at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle.
According to this, by providing a position where the division point distance is maximized at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle at which the volume becomes zero, the fluctuation of the compressive force immediately before the completion of compression is provided. At the same time, fluctuations in the compressive force in other compression chambers can be generated. As a result, the fluctuations in the compressive force can be canceled out between the compression chamber on the central side and the other compression chambers, and the reduction range of the compressive force can be reduced. As a result, sudden fluctuations in compressive force can be suppressed and vibration can be reduced.

Further, for the scroll type compressor, the division point distance at one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle is all the turning angles from the turning start angle to the turning end angle. It may be the maximum and the maximum among the division point distances in.

According to this, the compressive force can be changed more greatly at one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle, and the compression force fluctuates between the central compression chamber and the other compression chambers. Can be canceled and the reduction width of the compressive force can be reduced.

According to the present invention, it is possible to reduce the vibration caused by the fluctuation of the compressive force.

The vertical sectional view which shows the scroll type compressor of an embodiment. The figure which shows the fixed side swirl wall and the swirl side swirl wall of embodiment. An enlarged view showing the first end portion and the arc portion of the fixed side spiral wall and the swirl side spiral wall. The figure which shows the contact, the variable part, and the section point distance of a fixed side spiral wall and a swirl side spiral wall. The figure which shows the fixed side spiral wall and the swirl side spiral wall at the time of completion of compression. The figure which shows the central side compression chamber. A graph showing the relationship between the turning angle and the division point distance. A graph showing the relationship between the turning angle and the compressive force. The figure which shows the fixed side spiral wall and the swirl side spiral wall of a comparative example.

Hereinafter, an embodiment in which the scroll type compressor is embodied will be described with reference to FIGS. 1 to 9.
As shown in FIG. 1, the scroll type compressor 10 includes a housing 11 in which a suction port 11a for sucking a fluid and a discharge port 11b for discharging a fluid are formed. The housing 11 has a substantially cylindrical shape as a whole. The housing 11 has two parts 12 and 13 having a bottomed cylindrical shape. The first part 12 and the second part 13 are assembled with their open ends abutting each other. The suction port 11a is provided at a position on the side wall portion 12a of the first part 12, more specifically, at a position on the bottom portion 12b side of the first part 12 of the side wall portion 12a. The discharge port 11b is provided on the bottom portion 13a of the second part 13.

The scroll type compressor 10 includes a rotating shaft 14, a compression unit 15 that compresses the suction fluid sucked from the suction port 11a and discharges it from the discharge port 11b, and an electric motor 16 that drives the compression unit 15. .. The rotating shaft 14, the compression unit 15, and the electric motor 16 are housed in the housing 11. The electric motor 16 is arranged on the suction port 11a side in the housing 11, and the compression unit 15 is arranged on the discharge port 11b side in the housing 11.

The rotating shaft 14 is housed in the housing 11 in a rotatable state. Specifically, a shaft support member 21 that pivotally supports the rotating shaft 14 is provided in the housing 11. The shaft support member 21 is fixed to the housing 11 at a position between the compression unit 15 and the electric motor 16, for example. The shaft support member 21 is formed with an insertion hole 23 in which the rotating shaft 14 can be inserted and the first bearing 22 is provided. Further, the shaft support member 21 and the bottom portion 12b of the first part 12 face each other, and a cylindrical boss 24 projects from the bottom portion 12b. A second bearing 25 is provided inside the boss 24. The rotating shaft 14 is rotatably supported by both bearings 22 and 25.

The compression unit 15 includes a fixed scroll 31 fixed to the housing 11 and a swivel scroll 32 that swivels with respect to the fixed scroll 31 and is capable of revolving.
The fixed scroll 31 has a disk-shaped fixed-side substrate 31a provided on the same axis as the rotating shaft 14, and a fixed-side spiral wall 31b rising from the fixed-side substrate 31a. Similarly, the swivel scroll 32 includes a swirl side substrate 32a which is disk-shaped and faces the fixed side substrate 31a, and a swirl side swirl wall 32b which stands up from the swivel side substrate 32a toward the fixed side substrate 31a. There is.

The fixed scroll 31 and the swivel scroll 32 mesh with each other. Specifically, the fixed-side swirl wall 31b and the swirl-side swirl wall 32b are in mesh with each other, and the tip surface of the fixed-side swirl wall 31b is in contact with the swirl-side substrate 32a and the tip surface of the swirl-side swirl wall 32b. Is in contact with the fixed side substrate 31a. A compression chamber 33 for compressing the fluid is partitioned by the fixed scroll 31 and the swivel scroll 32.

FIG. 2 shows the time point at which the fluid was first confined in the compression chamber 33 by the fixed scroll 31 and the swivel scroll 32. At this point, the compression chamber 33 is the first compression chamber 33a formed by the inner peripheral side of the fixed side spiral wall 31b and the outer peripheral side of the swirling side swirl wall 32b, and the outer peripheral side and the swirling side swirl wall of the fixed side swirl wall 31b. Two of the second compression chambers 33b formed by the inner peripheral side of 32b are formed. A similar compression chamber is also partitioned inside the first compression chamber 33a and the second compression chamber 33b. Further, as shown in FIG. 6, as the swivel scroll 32 revolves, the first compression chamber 33a and the second compression chamber 33b are connected so that the central compression chamber 33c is formed in the central portion of the fixed scroll 31. It has become. Therefore, in the scroll type compressor 10, a plurality of compression chambers 33 are formed at the same time.

As shown in FIG. 1, the shaft support member 21 is formed with a suction passage 34 for sucking the suction fluid into the compression chamber 33. Further, the swivel scroll 32 is configured to revolve with the rotation of the rotation shaft 14. Specifically, a part of the rotating shaft 14 projects toward the compression portion 15 through the insertion hole 23 of the shaft support member 21. An eccentric shaft 35 is provided at a position of the end surface of the rotating shaft 14 on the compression portion 15 side that is eccentric with respect to the axis L of the rotating shaft 14. A bush 36 is provided on the eccentric shaft 35. The bush 36 and the swivel scroll 32 (specifically, the swivel side substrate 32a) are connected via a bearing 37.

Further, the scroll type compressor 10 includes a rotation regulation unit 38 that regulates the rotation of the rotation scroll 32 while allowing the revolution movement of the rotation scroll 32. A plurality of rotation control units 38 are provided. When the rotation shaft 14 rotates in a predetermined positive direction, the revolving motion of the swivel scroll 32 in the positive direction is performed. The swivel scroll 32 revolves in the positive direction around the axis of the fixed scroll 31 (that is, the axis L of the rotating shaft 14). As a result, the volume of the compression chamber 33 is reduced, so that the suction fluid sucked into the compression chamber 33 through the suction passage 34 is compressed. The compressed fluid is discharged from the discharge port 41 provided on the fixed-side substrate 31a, and then discharged from the discharge port 11b. The fixed-side substrate 31a is provided with a discharge valve 42 that covers the discharge port 41. The fluid compressed in the compression chamber 33 pushes away the discharge valve 42 and is discharged from the discharge port 41.

The electric motor 16 revolves the swivel scroll 32 by rotating the rotating shaft 14. The electric motor 16 includes a rotor 51 that rotates integrally with the rotating shaft 14, and a stator 52 that surrounds the rotor 51. The rotor 51 is connected to the rotating shaft 14. The rotor 51 is provided with a permanent magnet (not shown). The stator 52 is fixed to the inner peripheral surface of the housing 11 (specifically, the first part 12). The stator 52 has a stator core 53 that is radially opposed to the cylindrical rotor 51, and a coil 54 that is wound around the stator core 53.

The scroll type compressor 10 includes an inverter 55 as a drive circuit for driving the electric motor 16. The inverter 55 is housed in a cylindrical cover member 56 attached to the housing 11, specifically the bottom 12b of the first part 12. The inverter 55 and the coil 54 are electrically connected.

2 to 6 show only the fixed-side swirl wall 31b of the fixed scroll 31 and the swirl-side swirl wall 32b of the swivel scroll 32. The fixed-side spiral wall 31b and the swirl-side spiral wall 32b are spiral-shaped extending from the first end E located on the central side of the spiral toward the second end S located on the outer peripheral end of the spiral.

In the fixed-side spiral wall 31b and the swirl-side spiral wall 32b, the first end portion E is formed by the arc C as shown by the alternate long and short dash line in FIG. Further, as shown by the solid line in FIG. 3, the outer peripheral surfaces of the fixed side spiral wall 31b and the swivel side spiral wall 32b are formed by an involute curve from the second end portion S to one end of the arc C of the first end portion E. Has been done. Further, the inner peripheral surfaces of the fixed-side spiral wall 31b and the swivel-side spiral wall 32b are formed from the second end portion S to immediately before the first end portion E based on the involute curve, and are formed along the two-dot chain line in FIG. As shown, an arc is formed from the end point F of the involute curve to the other end of the arc C of the first end E. The arc formed between the end point F of the involute curve and the arc C of the first end E is referred to as the arc portion R. The arc portion R is an arc connected to the tip (first end portion E) of the fixed side spiral wall 31b and the swirl side spiral wall 32b. On the inner peripheral surfaces of the fixed-side spiral wall 31b and the swirl-side spiral wall 32b, the involute curve and the arc portion R are switched by the end point F.

The involute curve is a plane curve formed by the locus drawn by the tip of the normal when one normal set on the base circle is moved so as to always be in contact with the base circle, and is also called an involute. On the inner peripheral surfaces of the fixed-side spiral wall 31b and the swirl-side spiral wall 32b, the end point F immediately before the first end E corresponds to the start of winding of the involute curve, and the second end S corresponds to the end of winding of the involute curve. Corresponds to. Further, on the outer peripheral surfaces of the fixed-side spiral wall 31b and the swivel-side spiral wall 32b, one end of the arc C of the first end E corresponds to the start of winding of the involute curve, and the second end S corresponds to the end of winding of the involute curve. Applicable.

Immediately before the first end portion E, the arc portion R is formed on the inner peripheral surfaces of the fixed side spiral wall 31b and the swivel side spiral wall 32b in the central compression chamber 33c, as shown in FIG. This is to suppress fluid leakage when one first end E of the fixed side spiral wall 31b and the swirl side spiral wall 32b comes into contact with the inner peripheral surface of the other spiral wall.

Here, as shown in FIG. 2, the center of the base circle (not shown) of the involute curve drawn by the fixed-side spiral wall 31b is set as the center of the fixed-side base circle P1, and the base circle of the involute curve drawn by the swirl-side spiral wall 32b. The center (not shown) is the center of the foundation circle on the turning side P2. The straight line passing through both the fixed-side foundation circle center P1 and the turning-side foundation circle center P2 is defined as the radial direction line M. The radial direction line M is a straight line extending in the radial direction of the base circle.

As shown in FIGS. 2 to 5, there are a plurality of partition points T in which the fixed side spiral wall 31b and the swirl side spiral wall 32b are in contact with each other. The number of partition points T varies depending on the number of turns of the spiral walls 31b and 32b. The partition points T include a partition point between the outer peripheral surface of the swirl-side spiral wall 32b and the inner peripheral surface of the fixed-side spiral wall 31b, and an inner peripheral surface of the swirl-side spiral wall 32b and the outer peripheral surface of the fixed-side spiral wall 31b. A section point is formed. Then, as the revolving motion of the swivel scroll 32, the partition point T moves toward the first end portion E along the fixed side spiral wall 31b. Further, the first compression chamber 33a and the second compression chamber 33b are also displaced toward the first end portion E.

Assuming that the number of turns of the fixed side spiral wall 31b and the swivel side swirl wall 32b is about two and a half, they are formed on the second end S side of the fixed side swirl wall 31b and the swivel side swirl wall 32b as shown in FIG. When only one partition point T is moved to the first end portion E by following the spiral walls 31b and 32b, the partition point T also moves by about two and a half turns. When the position of the section point T along the spiral walls 31b and 32b is expressed as the turning angle of the turning scroll 32, the maximum value of the turning angle is expressed as the turning end angle. The turning angle is defined as the turning angle at the time when the partition point T is formed on the second end S side, that is, when the compression of the fluid confined in the compression chamber 33 is started.

Then, as shown in FIG. 5, when the turning angle reaches the turning end angle, the partition point T reaches the first end portion E of the fixed side spiral wall 31b and the turning side spiral wall 32b. The time when the partition point T reaches the first end portion E is the time when the volume of the central compression chamber 33c becomes zero and the compression of the fluid in the central compression chamber 33c is completed.

As shown in FIG. 4, the distance between the division point T and the radial direction line M is defined as the division point distance K. The section point distance K is specifically the length of a perpendicular line drawn from the section point T with respect to the radial direction line M. When the partition point T is located near the second end S of both spiral walls 31b and 32b, the partition point T and the radial direction line M are separated from each other, and the partition point distance K exists.

Further, as shown in FIG. 6, even when the central compression chamber 33c is formed, the partition point T and the radial direction line M are separated from each other, and the partition point distance K exists. Further, as shown in FIG. 5, at the time when one partition point T moves to the first end E of the fixed side spiral wall 31b and the swirl side spiral wall 32b, that is, at the turning end angle, the partition point T is a radial direction line. It is located on M, and the division point distance K becomes zero. However, the division point T located on the turning angle other than the turning end angle is separated from the radial direction line M, and the division point distance K exists.

The graph of FIG. 7 shows the relationship between the turning angle and the division point distance K. The partition point distance K suddenly increases (suddenly changes) before the completion of compression of the fluid by the central compression chamber 33c. This is a partition point T formed by contacting the first end E of the swirl side spiral wall 32b with the inner peripheral surface of the fixed side spiral wall 31b, and the inner peripheral surface of the swirl side spiral wall 32b is the fixed side swirl wall. This is because the position where the division point T is formed changes when each of the division points T formed in contact with the first end portion E of 31b moves from the involute curve to the arc portion R.

In the following description, the turning angle at the position where the contact between the first end portion E and the arc portion R is started is defined as the tip contact start angle. The tip contact start angle is such that the first end E of the swirl side spiral wall 32b contacts the arc portion R drawn on the inner peripheral surface of the fixed side swirl wall 31b before the compression in the central compression chamber 33c is completed. Is the turning angle to start. As shown in FIG. 3, the tip contact start angle is also the position where the position of the section point T is switched from the involute curve to the arc portion R at the end point F on the inner peripheral surfaces of the fixed side spiral wall 31b and the swivel side spiral wall 32b. be. Then, the division point distance K rapidly increases due to the movement of the division point T along the arc portion R after the division point T has passed the tip contact start angle, then decreases sharply, and becomes zero when the compression is completed. Hereinafter, the fluctuation range W of the turning angle is defined from the tip contact start angle to the turning end angle between the turning start angle and the turning end angle. This fluctuation range W is also a range in which the division point distance K fluctuates discontinuously.

Further, as shown in FIGS. 2 and 4 to 6, the fixed-side spiral wall 31b and the swirl-side spiral wall 32b have a variable portion H in which the wall thickness gradually changes on the second end portion S side of the arc portion R. Be prepared. The fluctuating portion H is closer to the second end S than the first end E and the arc portion R, and the wall thickness gradually increases from the second end S side toward the first end E, and then the arc. It has a shape that gradually becomes thinner toward the portion R so as to have the original thickness. Therefore, when the partition point T passes through the fluctuating portion H, the partition point distance K becomes longer than when the partition point T does not pass through the fluctuating portion H.

Here, the division point distance K from the turning start angle to the turning end angle will be described.
As shown in the graph of FIG. 7, the section point distance K does not fluctuate significantly from the turning start angle (0 °) at which the fluid compression starts, and gradually and continuously shortens. The reason why the division point distance K is gradually shortened is that the wall thicknesses of the fixed side spiral wall 31b and the swirl side spiral wall 32b are made as thin as the second end portion S, although not shown in detail. ..

In the range of the turning angle at which the division point T passes through the variable portion H, the division point distance K suddenly changes as shown by the solid line or the alternate long and short dash line in the graph of FIG. For example, as shown in FIGS. 2, 4 and 5, the division point distance K becomes longer as the division point T moves through the variable portion H. The variable portion H is formed at a position where the division point distance K is discontinuously increased or decreased before the time when the division point distance K becomes zero, that is, before the time when the compression is completed.

The range in which the variable portion H can be provided is represented by a turning angle. First, each turning angle obtained by subtracting an integral multiple (n) of 360 ° from the tip contact start angle is set as the first turning angle, and each turning angle obtained by subtracting an integral multiple (n) of 360 ° from the turning end angle is used as the second turning angle. Make a corner. The range of the turning angle in which the fluctuating portion H can be provided is set to the turning angle existing in the range from the first turning angle to the second turning angle. Note that n, which is an integral multiple of the subtraction, is the same integer for the tip contact start angle and the turning end angle, and is an integer equal to or less than the number of turns of the fixed side spiral wall 31b and the turning side spiral wall 32b. Then, the fluctuation unit H is set so that the division point distance K becomes maximum at at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning angle in the fluctuation range W.

In the present embodiment, the fluctuation unit H refers to one of the turning angles (second turning angle) from the turning start angle to the turning end angle, which is obtained by subtracting an integral multiple of 360 ° from the turning end angle. The section point distance K is set to be maximum. Specifically, the maximum value A at which the division point distance K is maximum and maximum is set at one second turning angle. In this case, the division point distance K becomes discontinuously and suddenly longer from the second end S side than one second turning angle obtained by subtracting an integral multiple of 360 ° from the turning end angle, and from the turning end angle. After reaching the maximum value A at the second turning angle minus an integral multiple of 360 °, it suddenly shortens toward the first end E.

As shown by the alternate long and short dash line in FIG. 7, the fluctuating portion H is the turning angle (first turning) from the turning start angle to the turning end angle, which is obtained by subtracting an integral multiple of 360 ° from the tip contact start angle. When the section point distance K is set to be maximum at (angle), the section point distance K is not from the second end S side of the first turning angle obtained by subtracting an integral multiple of 360 ° from the tip contact start angle. It suddenly becomes longer in a row. Then, after reaching the maximum (maximum value A) at the first turning angle obtained by subtracting an integral multiple of 360 ° from the tip contact start angle, the angle suddenly shortens toward the first end E.

Next, the relationship between the turning angle and the compressive force will be described. In the graph of FIG. 7, in the graph of FIG. 7, the turning scroll 32 revolves once from the time when the section point T begins to pass the curve of the arc portion R and the section point distance K begins to rapidly increase immediately before the completion of compression. The relationship between the turning angle and the compressive force is shown. The compressive force is the total of the reaction forces generated when the fluid is compressed in each compression chamber 33, and the more the fluid is compressed, the higher the compressive force becomes.

Here, FIG. 9 shows a fixed-side spiral wall 61 and a swirl-side spiral wall 62 of a comparative example in which the variable portion H is not provided and the wall thickness does not change suddenly. Then, in the graph of FIG. 7, the two-dot chain line shows the relationship between the division point distance K and the turning angle in the comparative example, and the two-dot chain line of the graph of FIG. 8 shows the relationship between the compressive force and the turning angle in the comparative example. ..

As shown by the two-dot chain line in the graph of FIG. 7, in the comparative example, the division point distance K suddenly changes even at the turning angle (second turning angle) obtained by subtracting 360 ° from the compression completion time (turning end angle). Not. Then, in the comparative example, as shown by the alternate long and short dash line in the graph of FIG. 8, a sharp decrease in the compressive force occurs immediately before the completion of compression.

On the other hand, in the present embodiment in which the variable portion H is set so that the maximum value A at which the division point distance K becomes maximum at the second turning angle comes, as shown in the solid line graph of FIG. 8, the compression is completed. When the division point distance K starts to increase immediately before, the compressive force gradually increases, and after the division point distance K reaches the maximum value B, it decreases toward the completion of compression. The reduction width of the compressive force is smaller than that.

Further, as shown in the graph of the alternate long and short dash line in FIG. 8, even when the variable portion H is set so that the maximum value A of the division point distance K comes to the first turning angle, the division point distance is immediately before the completion of compression. When K begins to increase, the compressive force gradually increases, and after the section point distance K reaches the maximum value B, it decreases toward the completion of compression, but the compressive force is higher than that of the comparative example. The reduction range is small.

Such a reduction in the reduction width of the compressive force is achieved by forming the variable portion H within a predetermined range until the swivel scroll 32 revolves from the tip contact start angle to the swivel end angle in the central compression chamber 33c. This is because the compression force is fluctuated by rapidly increasing the other compression chambers 33 so that the division point distance K becomes maximum. Then, at the same time that the compression force fluctuates in the central compression chamber 33c, the other compression chambers 33 (first compression chamber 33a and second compression chamber 33b) also generate fluctuations in the compression force to reduce the compression force. By canceling each other out, the compressive force is reduced.

In the present embodiment, n is set to 1, and the fluctuating portion H is provided at a turning angle in the fluctuating range W obtained by subtracting 360 ° from the time when compression is completed. Therefore, the partition point distance K immediately before the completion of compression in the central compression chamber 33c becomes zero, and at the same time, the partition point distance K is maximized for the other compression chambers 33 (first compression chamber 33a and second compression chamber 33b). The compression force is fluctuated by rapidly increasing so as to become. That is, at the same time that the compression force fluctuates in the central compression chamber 33c, the other compression chambers 33 (first compression chamber 33a and second compression chamber 33b) also generate fluctuations in the compression force to reduce the compression force. By canceling each other out, fluctuations in compressive force are reduced.

As a result, the fluctuation of the compressive force is canceled by causing the compression chamber 33 (the first compression chamber 33a and the second compression chamber 33b) other than the central compression chamber 33c to fluctuate 360 ° before the completion of the compression. , The reduction width of the compressive force is smaller than that of the comparative example.

According to the above embodiment, the following effects can be obtained.
(1) In the scroll type compressor 10, the fixed side spiral wall 31b and the swirl side spiral wall 32b are provided with variable portions H whose wall thickness is gradually changed. Further, the fluctuation portion H is provided at the turning angle obtained by subtracting 360 ° from the turning angle in the fluctuation range W, and the section is divided so that the division point distance K is maximized at the turning angle (as shown by the maximum value A). The point distance K was suddenly changed. Then, at the same time as the fluctuation of the compressive force in the central compression chamber 33c, the fluctuation of the compressive force is also generated in the other compression chambers 33 (first and second compression chambers 33a, 33b). As a result, fluctuations in the compressive force can be canceled out immediately before the completion of compression, and the reduction range of the compressive force can be reduced. Therefore, it is possible to suppress abrupt fluctuations in the compressive force, reduce the vibration of the scroll type compressor 10, and also reduce the noise caused by the vibration.

(2) The division point distance K is suddenly changed so that the division point distance K becomes the maximum (as shown by the maximum value A) at the turning angle obtained by subtracting 360 ° from the completion of compression, and the central compression chamber 33c is used. At the same time as the fluctuation of the compressive force, the fluctuation of the compressive force is also generated in the other compression chambers 33 (first and second compression chambers 33a and 33b). As a result, fluctuations in the compressive force can be canceled out immediately before the completion of compression, and the reduction range of the compressive force can be reduced. Therefore, it is possible to suppress abrupt fluctuations in the compressive force, reduce the vibration of the scroll type compressor 10, and also reduce the noise caused by the vibration.

(3) Focusing on the fluctuation of the division point distance K and the compressive force until the division point T reaches the first end portion S from the second end portion S, 360 ° is subtracted from the turning angle in the fluctuation range W. The division point distance K is suddenly changed so that the division point distance K becomes maximum at the turning angle (as shown by the maximum value A). Then, the reduction range of the compressive force at the time of completion of compression is reduced to suppress a sudden fluctuation of the compressive force. Since the partition point distance K can be adjusted by adjusting the wall thicknesses of the fixed-side spiral wall 31b and the swirl-side spiral wall 32b, the compressive force does not increase the size of the fixed-side spiral wall 31b and the swirl-side spiral wall 32b. Can suppress sudden fluctuations in. Further, since it is only necessary to adjust the wall thicknesses of the fixed-side spiral wall 31b and the swirl-side spiral wall 32b, fluctuations in the compressive force can be suppressed without adding other parts, for example.

(4) The value of the division point distance K of the maximum value A caused by the sudden change of the division point distance K corresponding to the fluctuation portion H is among the division point distances K at all the turning angles from the turning start angle to the turning end angle. It is the maximum. By adjusting the wall thickness of the fluctuating portion H so that such a division point distance K is formed, fluctuations in the compressive force can be effectively suppressed.

The above embodiment may be changed as follows.
○ Regardless of the number of turns of the fixed-side spiral wall 31b and the swivel-side spiral wall 32b, there may be only one place where the division point distance K is maximized, or there may be a plurality of places. For example, in the embodiment, the place where the division point distance K is maximum (for example, the place where the maximum value A of the division point distance K is shown) is obtained by subtracting 360 ° × 1 (n = 1) from the completion of compression at the turning angle. It may be both the turning angle obtained by subtracting 360 ° × 2 (720 °: n = 2), or it may be only before 720 °.

○ The number of places where the division point distance K is maximized may be changed according to the number of turns of the fixed side spiral wall 31b and the swivel side spiral wall 32b.
○ The value of the maximum value A when the division point distance K is suddenly changed may be smaller than the value of the maximum value B that appears immediately before the completion of compression.

○ In the embodiment, the division point distance K is defined as the distance between the point where the fixed-side spiral wall 31b and the swirl-side spiral wall 32b come into contact with each other to partition the compression chamber 33 and the radial direction line M, but the distance is not limited to this. If there is no fluid leakage through the gap, the point where the fixed-side spiral wall 31b and the swirl-side spiral wall 32b are close to each other to partition the compression chamber 33 is defined as a partition point, and the distance between this partition point and the radial direction line M is defined as a partition point. The point distance K may be set.

○ The maximum value A may appear as a continuous change in proximity point distance, not as a discontinuity.

E ... 1st end as an end, P1 ... fixed side foundation circle center, P2 ... swirl side foundation circle center, K ... division point distance, M ... radial direction line as a straight line, T ... division point, 10 ... scroll Mold compressor, 31 ... fixed scroll, 31a ... fixed side substrate, 31b ... fixed side swirl wall, 32 ... swivel scroll, 32a ... swivel side substrate, 32b ... swivel side swirl wall, 33 ... compression chamber.

Claims (3)

A fixed-side substrate and a fixed scroll having a fixed-side spiral wall erecting from the fixed-side substrate,
A swivel-side substrate facing the fixed-side substrate and a swivel scroll having a swirl-side swirl wall that stands up from the swivel-side substrate toward the fixed-side substrate and meshes with the fixed-side swirl wall. In a scroll type compressor in which a swirl scroll swivels to compress a fluid in a compression chamber partitioned by the fixed scroll and the swirl scroll.
A straight line passing through both the center of the base circle of the involute curve drawn by the fixed-side spiral wall and the center of the base circle of the involute curve drawn by the swirl-side spiral wall.
The distance between the fixed-side spiral wall and the point where the swirl-side spiral wall comes into contact with or is close to each other to partition the compression chamber is defined as a partition point distance.
Regarding the swirl angle of the swirl scroll, the swirl angle at which the compression chamber is formed and the compression of the fluid is started is set as the swirl start angle, the swirl angle at which the fluid compression is completed is set as the swirl end angle, and before the compression is completed. The turning angle at which the end of the swirl wall on the swivel side is connected to the tip of the swirl wall on the fixed side and starts contacting a part of the inner peripheral surface that draws an arc is defined as the tip contact start angle.
Regarding the relationship between the turning angle and the division point distance, an integer of 360 ° from the turning angle in the range from the turning start angle to the turning end angle and from the tip contact start angle to the turning end angle. A scroll type compressor characterized in that the division point distance is maximized at at least one of the turning angles obtained by subtracting double. The scroll type compressor according to claim 1, wherein the division point distance is maximized at at least one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle. The division point distance at one of the turning angles obtained by subtracting an integral multiple of 360 ° from the turning end angle is the maximum and maximum among the division point distances at all turning angles from the turning start angle to the turning end angle. The scroll type compressor according to claim 2.

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