KR101012052B1 - Scroll compressor - Google Patents

Abstract

An object of the present invention is to stabilize the swinging motion of the rocking scroll while suppressing the starting load of the scroll compressor.

MEANS TO SOLVE THE PROBLEM In order to solve the said subject, according to this invention, the slide which makes a predetermined angle with respect to the load direction of the gas in the compression chamber 25 in the eccentric shaft 23 of the rotating shaft 5 which drives the rocking scroll 8 is carried out. In the scroll compressor (C) which is comprised so that the eccentricity of the eccentric shaft 23 may become large when the load of the gas in the compression chamber 25 is applied through the slide bush 27 which has the surface 90, The slide A spring member 95 is inserted between the bush 27 and the eccentric shaft 23, and is always biased so that the amount of eccentricity of the eccentric shaft 23 becomes small. The spring member 95 has an eccentric shaft 23. Is pressed against the slide surface 90 of the slide bush 27.

Scroll compressor, slide bush, eccentric shaft, spring member, rocking scroll

Description

Scroll Compressor {SCROLL COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a scroll compressor for engaging a plurality of compression chambers by engaging each of the wraps formed on opposite surfaces of the fixed scroll and the hard plate of the swinging scroll that pivots about the fixed scroll.

Conventionally, this type of scroll compressor has fixed scrolls and rocking scrolls that pivot about the fixed scrolls, and forms spiral wraps on opposite surfaces of the hard plates of the fixed scrolls and rocking scrolls, respectively, so that each wrap can It is comprised so that it may engage and form several compression chamber.

A slide bush is interposed on the eccentric shaft of the rotating shaft for driving the rocking scroll. This slide bush has a slide surface which forms a predetermined angle with respect to the load direction of the gas in a compression chamber, and is comprised so that the amount of eccentricity of an eccentric shaft may become large when the load of the gas in a compression chamber is applied.

According to such a structure, since the component of gas load can act to increase the eccentric amount by the slide surface, the sealing property between both the laps of a fixed scroll and a rocking scroll can be improved, and the performance of a compressor can be improved. It is known (for example, refer patent document 1).

In such a scroll compressor, a spring member is inserted between the slide bush and the eccentric shaft, the eccentric shaft is pushed in the eccentric direction by the spring member (that is, pressed), and the amount of eccentricity at startup is reduced to reduce the load at startup. It is also developed.

Specifically, in the scroll compressor, by pressing the eccentric shaft in the eccentric direction by the spring member, the amount of eccentricity is small at the time of stopping and the clearance of both laps is increased, so that the starting load can be reduced.

On the other hand, when the gas load starts to be applied, the slide bush moves in the direction of increasing the eccentricity of the eccentric shaft against the bias force of the spring member. See Document 2.

[Patent Document 1] Japanese Unexamined Patent Publication No. 7-71386

[Patent Document 2] Japanese Patent No. 3165153.

However, in the scroll compressor in which the eccentric shaft is pressed in the eccentric direction by the spring member and the eccentric amount of the eccentric shaft is variable, the sliding surface of the slide bush and the eccentric shaft fall during operation, so that a double gap occurs. There was a problem.

This invention is made | formed in order to solve such a conventional technical subject, and it aims at stabilizing the rotational motion of a rocking scroll, suppressing the starting load of a scroll compressor.

The scroll compressor according to the first aspect of the present invention has a fixed scroll and a swinging scroll which pivots about the fixed scroll, and forms spiral wraps on opposite surfaces of the hard plates of the fixed scroll and the swinging scroll, respectively. The plurality of compression chambers together to form a plurality of compression chambers, and a compression bush having a slide bush having a slide surface at a predetermined angle with respect to the load direction of the gas in the compression chamber on the eccentric shaft of the rotating shaft for driving the swinging scroll. When the gas load is applied, the eccentricity of the eccentric shaft is increased, and is provided between the slide bush and the eccentric shaft, and is provided with a spring member that always biases the eccentric amount of the eccentric shaft so that the spring member is eccentric. And press the shaft against the slide surface of the slide bush.

The scroll compressor according to the second aspect of the present invention, in the invention described in the first aspect, has a spring accommodating portion formed on an inner surface of the slide bush for accommodating a spring member, and a spring member on the swinging scroll side of the spring accommodating portion. It is characterized in that the closing portion is formed to regulate the movement of.

According to the present invention, a fixed scroll and a swinging scroll which pivots about the fixed scroll, spiral wraps are formed on opposite surfaces of the fixed scroll and the swinging plate of the rigid plate, and the respective wraps are engaged with each other to form a plurality of compressions. When the chamber is formed and a slide bush having a slide surface having a predetermined angle with respect to the load direction of the gas in the compression chamber is applied to the eccentric shaft of the rotating shaft that drives the swinging scroll, and the gas load in the compression chamber is applied. In the scroll compressor configured to increase the amount of eccentricity of the eccentric shaft, the scroll compressor is inserted between the slide bush and the eccentric shaft and is always biased so as to reduce the amount of eccentricity of the eccentric shaft. Clearance of the liver increases, and the load at start-up can be reduced.

In addition, when the scroll compressor starts to operate, the slide bush is generated by a predetermined angle with respect to the gas load direction of the slide surface, and moves in a direction in which the amount of eccentricity of the eccentric shaft is increased. have.

In addition, since the spring member presses the eccentric shaft against the slide surface of the slide bush, the eccentric shaft can be pressed against the slide surface of the slide bush at all times and can be in close contact. This makes it possible to reliably solve the problem that the sliding surface of the slide bush is separated from the eccentric shaft, so that double displacement occurs.

As a whole, it is possible to stabilize the swinging motion of the rocking scroll while suppressing the starting load, thereby improving the performance and reliability of the scroll compressor.

In particular, in the invention of the second aspect of the present invention, in the invention described in the first aspect, the spring is provided on the inner surface of the slide bush to accommodate the spring member, and the spring is provided on the swinging scroll side of the spring accommodation portion. Since the closure part which controls the movement of a member is formed, the problem that a spring member protrudes to the rocking scroll side by the said closure member can be avoided beforehand.

The present invention provides a scroll compressor in which a spring member is inserted between a slide bush and an eccentric shaft, the eccentric shaft is pushed in an eccentric direction by a spring member, and the eccentric amount of the eccentric shaft is variable. It was made to solve the problem of unstable rotational movement of rocking scroll, which is caused by the falling of the shaft. In this way, the objective of stabilizing the swinging motion of the swinging scroll while suppressing the starting load of the scroll compressor is always emphasized between the slide bush and the eccentric shaft so that the amount of eccentricity of the eccentric shaft becomes smaller, and the eccentric shaft of the slide bush This is achieved by inserting a spring member that presses against the slide surface. EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described in detail based on drawing.

Example 1

1 is a longitudinal side view of an embodiment of a scroll compressor to which the present invention is applied, and FIG. 2 shows an exploded view of the periphery of the eccentric shaft 23 of the rotary shaft 5. In Fig. 1, reference numeral 1 denotes a sealed container. This hermetically sealed container 1 is a container body 1A having a long cylindrical shape in the longitudinal direction, and an end cap 1B having a substantially bowl shape welded and fixed to both ends (both upper and lower ends) of the container body 1A, respectively. And the bottom cap 1C.

And the partition plate 10 which divides the space in the said sealed container 1 up and down is provided in the upper side in this sealed container 1 ,. That is, the inside of the airtight container 1 is partitioned into the upper space 11 and the lower space 12 by the partition plate 10. As shown in FIG.

In the lower space 12 in the hermetic container 1, a compression element 2 is placed above and a transmission element 3 as a drive means for driving the compression element 2 below is housed, respectively. In addition, the lower portion of the lower space 12 (that is, the inner surface of the bottom cap 1C) 65 is an oil pool in which lubricating oil for lubricating the compression element 2 and the like is stored. In the sealed container 1 between the compression element 2 and the transmission element 3, a support frame 4 is accommodated, and the support frame 4 has a bearing portion 6 and a boss accommodation portion at the center thereof. (22) is formed. This bearing part 6 is for supporting the front end (upper end) side of the rotating shaft 5, and is protruding downward from the center of one side (lower surface) of the said support frame 4, and is formed. Moreover, the boss accommodating part 22 is for accommodating the boss 24 of the swinging scroll 8 mentioned later, and is formed by recessing the center of the other surface (upper surface) of the support frame 4 downward. .

Moreover, the eccentric shaft 23 is formed in the front end (upper end) of the said rotating shaft 5. The center of the eccentric shaft 23 is eccentric with the shaft center of the rotary shaft 5, and is pivotally inserted into the boss 24 via the slide bush 27 and the swing bearing 28.

The compression element 2 is composed of a fixed scroll 7 and a rocking scroll 8. The fixed scroll 7 comprises a disk-shaped hard plate 14 and a spiral wrap formed of an involute shape or a curve approximated to one side (lower surface) of the hard plate 14. (15), a circumferential wall 16 provided so as to surround the lap 15, and a circumference of the circumferential wall 16, the outer periphery of which is the container body 1A of the sealed container 1 The flange 17 is fitted to the inner surface of the. In the center portion of the hard plate 14 of the fixed scroll 7, a discharge hole 18 communicating with the upper space 11 in the upper sealed container 1 partitioned by the partition plate 10 is formed. In addition, the fixed scroll 7 faces the protrusion direction of the wrap 15 downward.

In the structure of this embodiment, the hard plate 14 of the fixed scroll 7 discharges to the other surface (upper surface) of the said hard plate 14, and the cylindrical protrusion part 30 with the discharge hole 18 is carried out. It is provided. And this protrusion part 30 is fitted in the holding hole 10A formed in the said partition plate 10, and the upper surface 30A of the upper part of the said protrusion part 30 is the upper space 11 of the partition plate 10. It is configured to face). 30 A of upper surfaces of this protrusion part 30 are provided with the discharge valve 32 which opens and closes the discharge hole 18, and the some release valve 34 adjacent to this discharge valve 32. As shown in FIG. The release valve 34 is provided to prevent overcompression of the refrigerant, and communicates with a compression space (compression chamber 25) described later in the compression process via a release port (not shown).

Specifically, when the refrigerant pressure in the compression process reaches the discharge pressure before reaching the discharge hole 18, the release valve 34 is opened, and the refrigerant in the compression space 25 is discharged to the outside via the release port. .

On the other hand, the swinging scroll 8 is a scroll which pivots about the fixed scroll 7 described above, and an involute provided on a disk-shaped hard plate 20 and one surface (upper surface) of the hard plate 20. It consists of the spiral wrap 21 which consists of a shape or a curve approximating this, and the above-mentioned boss 24 formed in the center of the other surface (lower surface) of the hard board 20. As shown in FIG. Then, the swinging scroll 8 is disposed so that the lap 21 rotates 180 degrees with the lap 15 of the fixed scroll 7 to face the interlocking direction, with the protruding direction of the lap 21 upward. A plurality of compression spaces are formed between the wraps 15 and 21.

That is, the lap 21 of the swinging scroll 8 is engaged with the lap 15 of the fixed scroll 7 so that the front end surfaces of both the laps 21 and 15 are in contact with the bottom of the opponent, In addition, since the swinging scroll 8 is fitted to the eccentric shaft 23 provided eccentrically from the axial center of the rotation shaft 5, the two helical wraps 21 and 15 are eccentric with each other, A plurality of spaces confined in contact with each other on a ship are made, and each of these spaces becomes a compression chamber 25.

As for the said fixed scroll 7, the flange 17 provided around the circumference wall 16 is being fixed to the support frame 4 via the some bolt 37. In addition, the swinging scroll 8 is supported by the support frame 4 via an Oldham ring 40. The Oldham ring 40 is for orbiting the circular orbital image so that the swinging scroll 8 does not rotate with respect to the fixed scroll 7, and a pair of Oldham's keys formed by protruding upwards at positions facing each other. (41) and (41).

These Oldham keys 41 and 41 are slidably engaged with a key groove 42 formed in the lower surface of the fixed scroll 7. In this case, the Oldham ring 40 slides along the extension direction of the Oldham key 41 in the sliding space 43 formed between the fixed scroll 7 and the support frame 4 as the swinging scroll rotates.

In addition, since the swinging scroll 8 eccentrically revolves with respect to the fixed scroll 7, the eccentric direction and the contact position of the two spiral wraps move while rotating, and the compression chamber is moved from the outside to the compression chamber ( Zoom out while moving toward 25). First, the low-pressure refrigerant gas that enters and confines from the outer compression chamber 25 moves inward while being adiabatically compressed, and when it reaches the central portion, it becomes a high-temperature, high-pressure refrigerant gas. This refrigerant gas is sent to the upper space 11 via the discharge hole 18 formed in the said central part.

On the other hand, the transmission element 3 is composed of a stator 50 fixed to the sealed container 1 and a rotor 52 disposed inside the stator 50 and rotating in the stator 50. The rotating shaft 5 is fitted to the center of this rotor 52. The end (lower end) of the rotating shaft 5 is axially supported by the bearing 9 arranged at the bottom of the sealed container 1.

Moreover, the flow path 60 is formed in the inside of the rotating shaft 5 along the axial direction of the said rotating shaft 5. The flow path 60 includes a suction port 61 located at the lower end of the rotation shaft 5 and a paddle 63 formed above the suction port 61. The lower end of the rotating shaft 5 is immersed in the lubricating oil stored in the oil holding part 65, and the suction port 61 of the flow path 60 opens in the lubricating oil. In addition, the oil passage 60 is provided with an oil supply port 64 for lubricating oil at a position corresponding to each bearing. By this structure, when the rotating shaft 5 rotates, the lubricating oil stored in the oil holding part 65 enters the flow path 60 from the inlet 61 of the rotation shaft 5, and the paddle 63 of this flow path 60 is carried out. ) Is spread upward. Then, the lubricated oil is supplied to the sliding portion of each bearing or compression element 2 via each oil supply port 64 or the like.

On the other hand, the sealed container 1 is compressed by the refrigerant introduction pipe 67 for introducing the refrigerant into the lower space 12 in the sealed container 1 and the compression element 2, and the discharge hole ( A refrigerant discharge tube 68 for discharging the refrigerant discharged into the upper space 11 in the sealed container 1 to the outside via 18 is provided. In this embodiment, the refrigerant introduction pipe 67 is welded and fixed to the side surface of the container body 1A of the sealed container 1, and the refrigerant discharge pipe 68 is welded and fixed to the side surface of the end cap 1B.

An annular ring groove 70 is formed in the upper surface of the support frame 4 around the boss accommodating portion 22, and the ring groove 70 has a thrust ring formed of an iron-based sintered member ( 72 is arranged. This thrust ring 72 supports the hard plate 20 of the swinging scroll 8 and reduces the sliding resistance between the swinging scroll 8 and the support frame 4 when the swinging scroll 8 is pivoted. It is for. On the lower surface of the trust ring 72, a positioning pin 73 protrudes, and the positioning pin 73 is inserted into a coupling hole (not shown) formed in the ring groove 70. For this reason, even when the swinging scroll 8 has rotated on the thrust ring 72, the thrust ring 72 is supported by the positioning pin 73 in a state where the rotation of the thrust ring 72 is prevented. It is positioned in the frame 4.

In addition, in the structure of this embodiment, the rocking scroll 8 is supported movably in the axial direction toward the fixed scroll 7, and the lower surface (backside) of the thrust ring 72 when the compression element 2 is driven. By introducing the refrigerant of the compression process by the compression element 2 into the), the swinging scroll 8 can be pressed against the fixed scroll 7 via the thrust ring 72.

Specifically, a back space 75 through which the refrigerant in the compression process is introduced is formed between the thrust ring 72 and the support frame 4. Moreover, in order to ensure the airtightness of the back space 75, the O-ring which is not shown in figure is arrange | positioned in the inner periphery and the outer periphery of the thrust ring 72, respectively. In addition, in the swinging scroll 8 and the thrust ring 72, communication holes 78 communicating with the compression chamber 25 and the back space 75 are formed.

An opening of one end (upper end) of the communication hole 78 is formed at a position communicating with the compression chamber 25 at an intermediate pressure on the upper surface (lap surface) of the hard plate 20 of the swinging scroll 8. . This intermediate pressure is set to a value closer to the suction pressure.

On the other hand, the opening part of the other end (lower end) of the communication hole 78 is formed in the lower surface of the thrust ring 72, and is formed so that it may communicate with the back space 75, and the compression chamber 2 at the time of the drive of the compression element 2 is carried out. It is comprised so that the intermediate pressure of 25 may always be introduce | transduced into the back space 75. As shown in FIG. Thereby, the rocking scroll 8 can be squeezed stably to the fixed scroll 7 via the thrust ring 72.

On the other hand, a slide bush 27 is interposed on the eccentric shaft 23 of the rotation shaft 5. This slide bush 27 has a slide surface 90 as shown in FIGS. The slide surface 90 is formed in the slide bush 27 so as to form a predetermined angle with respect to the load direction of the gas in the compression chamber 25. Specifically, in the present embodiment, as shown in Figs. 5 and 7, the slide surface is inclined at a predetermined angle α from the eccentric direction (arrow D2) orthogonal to the load direction of the gas (arrow D1). 90 is formed. According to such a structure, when the gas load in the compression chamber 25 is applied, the slide surface 90 can act to increase the eccentricity of the gas load component. Thereby, the sealing property between both the laps of a fixed scroll and a rocking scroll can be improved, and the performance of the scroll compressor C can be improved.

3 is an enlarged view of the slide bush 27, FIG. 4 is a plan sectional view showing the state of the rotary shaft 5 at the start, FIG. 5 is a plan sectional view of the eccentric shaft 23 of FIG. 7 is a plan sectional view showing the state of the rotating shaft 5 in FIG. 7, and FIG. 7 shows a plan sectional view of the eccentric shaft 23 in FIG. 6, respectively. In FIG. 2, 91 is formed in surface 5A of the eccentric shaft 23 side of the rotating shaft 5 in order to absorb the process residue at the time of forming the slide surface 90 in the eccentric shaft 23. In FIG. It is an escape.

By the way, in such a scroll compressor, the spring member is inserted between the slide bush and the eccentric shaft, the eccentric shaft is pushed in the eccentric direction by the spring member, the amount of eccentricity at the start is reduced, and the load at the start is also reduced. have. Specifically, in the scroll compressor, by pressing the eccentric shaft in the eccentric direction by the spring member, the amount of eccentricity is small at the time of stopping and the clearance of both laps is increased, so that the starting load can be reduced. On the other hand, when the gas load starts to be applied, the slide bush moves in the direction of increasing the amount of eccentricity of the eccentric shaft in response to the pressing force of the spring member, so that an appropriate amount of eccentricity can be obtained.

However, in the scroll compressor in which the eccentric shaft is pressed in the eccentric direction by the spring member and the eccentric amount of the eccentric shaft is variable, the direction in which the eccentric shaft is biased coincides with the eccentric direction of the eccentric shaft, and the eccentric shaft is pressed against the slide surface. I could not. For this reason, there existed a problem that a double space | interval occurred when the slide surface of an slide bush and an eccentric shaft fell at the time of operation.

Therefore, in view of such a problem, in the present invention, the spring member (plate spring) 95 of the present invention is provided between the slide bush 27 and the eccentric shaft 23. This spring member 95 always biases the eccentric shaft 23 so that the amount of eccentricity of the eccentric shaft 23 becomes smaller like the conventional spring member mentioned above. However, the above-mentioned conventional spring member pushes the eccentric shaft in the eccentric direction, that is, the direction orthogonal to the load direction of the gas, whereas the spring member 95 of the present invention slides the eccentric shaft 23. It presses against the slide surface 90 of the bush 27.

Here, the specific structure is demonstrated using FIGS. 2-7. In each figure, reference numeral 95 denotes a spring member of the present embodiment to which the present invention is applied. This spring member 95 is comprised by the leaf spring curved to R shape. Further, 97 is a spring receiving portion formed on the inner surface of the slide bush 27, and 98 is a closing portion for restricting the movement of the spring member 95 (Fig. 3). The spring accommodating part 97 is formed by recessing the inner surface of the slide bush 27, ie, a part of the surface adjacent to the eccentric shaft 23 in the axial center direction (outer circumferential direction). Moreover, the said closed part 98 is formed in the rocking scroll 8 side of the spring accommodating part 97, and the rocking scroll 8 in the state which the spring member 95 was accommodated in the spring accommodating part 97. The side is supposed to be closed by the closure 98. Thereby, the problem that the spring member 95 sticks out to the swinging scroll 8 side can be avoided beforehand.

In this case, the spring member 95 is to be able to pressurize the eccentric shaft 23 at all times so as to press the slide bush 27 in the spring receiving portion 97. In particular, in the present invention, the spring member 95 is provided so as to press the eccentric shaft 23 against the slide surface 90 of the slide bush 27. In the present embodiment, the spring receiving portion 97 presses the eccentric shaft 23 against the slide surface 90 of the slide bush 27 when the spring member 95 is accommodated in the spring receiving portion 97. The slide bush 27 is formed in the positional relationship which can be biased.

In the structure of this embodiment, when the spring member 95 is accommodated in the spring accommodating part 97, the force which pushes the eccentric shaft 23 in the direction of the arrow D3 shown to FIG. 5 and FIG. The direction (arrow D3) of the force (hereinafter referred to as " side force ") that the spring member 95 presses the eccentric shaft 23 is eccentric direction D2, as is also clear from Figs. To form a predetermined angle. This angle is provided in the direction in which the eccentric shaft 23 is always pressed against the slide surface 90 of the slide bush 27. In this embodiment, the subordinate forces in the direction of arrow D3 are the force in the direction (arrow D4 shown in Figs. 5 and 7) for pressing the slide surface 90, and the eccentric direction (Figs. 5 and Fig. 7). It acts by dividing by the force of arrow (D2) shown in FIG. That is, the eccentric shaft 23 can be urged to always press the slide surface 90 of the slide bush 27 by the component force which generate | occur | produced in the direction (arrow D4) which presses the slide surface 90, By the component force generated in the eccentric direction (arrow D2), the eccentric shaft 23 can always be urged so that the amount of eccentricity of the eccentric shaft 23 becomes small.

On the other hand, the spring member 95 is configured such that a gap is formed on the outer circumferential surface of the spring member 95 and the wall surface of the spring receiving portion 97 facing the outer circumferential surface in the state accommodated in the spring receiving portion 97. In the present embodiment, the spring member 95 is formed such that a gap is formed on the outer circumferential surface of the spring member 95 and the wall surface of the spring receiving portion 97 facing the outer circumferential surface while the spring member 95 is accommodated in the spring receiving portion 97. ) And the radius of curvature of the spring accommodating part 97 are set.

Specifically, the radius of curvature of the spring member 95 before the spring member 95 is accommodated in the spring accommodating part 97 (when the leaf spring is opened) is set to R0, and the spring member 95 is the spring accommodating part. In the state accommodated in the 97, the gas load in the compression chamber 25 is not applied to the spring member 95, that is, the radius of curvature of the spring member 95 when the scroll compressor C is stopped. If the radius of curvature of the spring member 95 when R1 and the gas load in the compression chamber 25 is applied to the spring member 95 (during operation) is R2 and the radius of curvature of the spring accommodating portion 97 is R3, It is set in advance so that R3 is smaller than R0, R1 and R2. That is, since the curvature radii R0, R1 and R2 of the spring member 95 are larger than the curvature radii R3 of the spring accommodating part 97, the spring accommodating part ( A gap is necessarily formed between 97 and the spring member 95.

With the above structure, the operation | movement of the spring member 95 at the time of the stop of the scroll compressor C, and during operation is demonstrated. First, since the gas load is not applied at the time of stopping the scroll compressor C (similar to the starting attempt), the eccentric shaft 23 is in the state shown in Figs. 4 and 5 by the biasing force of the spring member 95. do. And the scroll compressor C starts from this state. In this arrangement relationship, since the eccentricity of the eccentric shaft 23 is small and the clearance between both wraps is large, compression is hardly achieved. Thereby, the load at the time of starting can be made small.

Then, when the scroll compressor C starts to operate, and the load of the gas in the compression chamber 25 begins to be applied, the slide bush 27 has a predetermined angle with respect to the gas load direction of the slide surface 90. The component force is generated by (component of gas load). That is, when the scroll compressor C starts to operate, the load of the gas in the compression chamber 25 is applied to the direction orthogonal to the eccentric direction, but the slide surface 90 is formed to have a predetermined angle with the direction of the gas load. Since the slide bush 27 is produced by a predetermined angle with respect to the gas load direction of the slide surface 90, the slide bush 27 is increased, and the amount of eccentricity of the eccentric shaft 23 is increased against the bias force of the spring member 95. Move in the direction of

Thus, when the slide bush 27 moves in the direction in which the eccentric amount of the eccentric shaft 23 increases, it will be in the state shown to FIG. 6 and FIG. As a result, an appropriate amount of eccentricity is obtained during operation. In this case, the spring member 95 is pushed toward the spring accommodating part 97 side by gas load and extends slightly, so that the radius of curvature R2 becomes smaller than the radius of curvature R1 at rest (that is, R0> R1> R2). ). However, even during this operation, the radius of curvature R2 of the spring member 95 is larger than the radius of curvature R3 of the spring accommodating portion 97 (ie, R0> R1> R2> R3). A gap is maintained between the member 95 and the spring receiving portion 97.

And even during this operation (that is, always), since the eccentric shaft 23 is pressed against the slide surface 90 by the spring member 95, the slide surface 90 of the eccentric shaft 23 and the slide bush 27 is carried out. ), Keep in close contact with. This can reliably solve the problem that the slide surface 90 and the eccentric shaft 23 of the slide bush 27 are separated and a double space is generated.

As described above in detail, the present invention can stabilize the swinging motion of the swinging scroll 8 while suppressing the load at start-up. Thereby, the performance and the reliability of the scroll compressor C can be improved.

In addition, as described above, the spring member 95 is accommodated in the spring accommodating part 97 by the closing part 98 formed on the oscillating scroll 8 side of the spring accommodating part 97. 8) Since the side is closed by the closing part 98 and movement is restricted, the problem that the spring member 95 sticks out to the swinging scroll 8 side can be avoided beforehand. Thereby, the reliability of the scroll compressor C can be improved further.

1 is a longitudinal side view (Example 1) of one embodiment of a scroll compressor;

2 is an exploded view of an eccentric shaft periphery of the rotating shaft of the scroll compressor of FIG.

3 is an enlarged view of the slide bush of FIG. 2;

4 is a plan sectional view of the eccentric shaft provided with the spring member of the present invention (at startup);

5 is an enlarged view of FIG. 4;

Fig. 6 is a sectional plan view (during operation) of an eccentric shaft having a spring member of the present invention;

7 is an enlarged view of FIG. 6.

<Description of the symbols for the main parts of the drawings>

C: scroll compressor 1: hermetic container

1A: container body 1B: end cap

1C: bottom cap 2: compression element

3: transmission element 4: support frame

5: rotating shaft 6: bearing part

7: fixed scroll 8: rocking scroll

9: bearing 10: partition plate

10A: retaining hole 11: upper space

12: lower space 14, 20: slab

15, 21: Lap 16: Perimeter Wall

17: flange 18: discharge hole

22: boss accommodating 23: eccentric shaft

24: boss 25: compression chamber

27: slide bush 28: slewing bearing

30: projection 30A: upper surface

32: discharge valve 34: release valve

37: Bolt 40: Oldham Ring

41: Oldham Key 42: Key Home

43: sliding space 50: stator

52: rotor 60: euro

61: inlet 63: paddle

64: oil inlet 65: oil pile

67: refrigerant introduction pipe 68: refrigerant discharge pipe

70: ring groove 72: trust ring

73: positioning pin 75: back space

78: communication hole 90: slide surface

91: escape portion 92: spring receiving portion

93: closure 95: spring member (plate spring)

97: spring receiving portion 98: closing portion

Claims (2)

A spiral wrap having a fixed scroll and a swinging scroll which pivots about the fixed scroll, and respectively forming spiral wraps on opposite surfaces of the hard plate of the fixed scroll and the swinging scroll to engage each wrap to form a plurality of compression chambers. At the same time, when the load of the gas in the compression chamber is applied to the eccentric shaft of the rotating shaft for driving the swinging scroll with a slide bush having a slide surface at a predetermined angle with respect to the load direction of the gas in the compression chamber. In the scroll compressor configured to increase the amount of eccentricity of the eccentric shaft, A spring member inserted between the slide bush and the eccentric shaft, the spring member being biased at all times so as to reduce the amount of eccentricity of the eccentric shaft, the spring member biasing the eccentric shaft against the slide surface of the slide bush. Characterized by a scroll compressor. The method according to claim 1, wherein the inner side of the slide bush is provided with a spring accommodating portion for accommodating the spring member, and the closing portion for regulating the movement of the spring member is formed on the swinging scroll side of the spring accommodating portion. Characterized by a scroll compressor.

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