KR101300597B1 - Scroll fluid machine - Google Patents

Abstract

In the scroll fluid machine which drives the pivoting scroll 10 by the rotational shaft 102 rotatably supported by the casing 100, and the rotational shaft 104 eccentrically rotatably supported by the rotational shaft 102, As one method, the anti-rotation plate 109 is attached to one end of the pivot shaft 104, and the anti-rotation pin 110 is attached to the anti-rotation plate 109. The anti-rotation pin 110 is pivoted while being inscribed in the anti-rotation bearing (guide mechanism) 111. As another method, the outer circumferential surface of one end 104b of the pivot shaft is pivoted while inscribed in the balance bearing (guide mechanism) 51. In this way, the eccentric swing-driven swing scroll enables the high speed operation of the scroll fluid machine because the swing scroll does not generate whirling motion.

Description

  Scroll Fluid Machine {SCROLL FLUID MACHINE}

The present invention relates to an eccentric swing drive scroll fluid machine suitable for high speed operation.

The scroll fluid machine has an actuating part constituted by combining a fixed scroll in which a spiral wrap is vertically provided on a hard plate, and a similar swing scroll. By fixing the swing scroll to the axis of the drive device and rotating it without rotating, the working fluid flowing into the suction pipe is compressed and discharged from the discharge pipe to function as a compressor or blower. Inflating and discharging the high pressure working fluid entering the fixed scroll inlet serves as an inflator powered by the drive shaft.

As a drive device used for a scroll fluid machine, an eccentric swing drive device having a swing axis has been proposed. For example, the scroll fluid machine disclosed by Japanese Patent Publication JP, 3761503, B (Registration Date: 2006.1.20) has an eccentric swing drive device and a fluid machine body driven by it. The pivot axis of the eccentric pivot drive device rests through the pivot scroll of the fluid machine body. Both circumferential scrolls have first and second eccentric pivot support means for eccentrically pivoting the pivot axis relative to the fixed scroll of the fluid machine body.

In this scroll fluid machine, swing bearings are provided on both sides of the swing scroll to support the swing shaft. On the outer side of both slewing bearings, rotary bearings are provided through a rotating body in which the rotational axis and the axis of the eccentric swing drive device coincide. Therefore, although the rotary bearing is driven by the pivot shaft at the time of operation | movement, since the mechanism which rotates both swing bearings synchronously is not provided, the rotational resistance of a rotary bearing and a swing bearing is applied to the movement direction of a pivot shaft. As a result, smooth driving of the pivot shaft may be hindered, and the wraps may come into contact with each other to generate noise, or the wraps may be worn or burned. An object of the present invention is to provide a structure that can prevent the whirling (whirling motion) to be smoothly driven while the pivot shaft is smoothly driven, and does not come in contact between the wraps, and to prevent noise or wear and burn traces of the wraps.

The present invention has been made to solve the above problems. The most important feature of the present invention is to provide a highly reliable scroll fluid machine, which has a structure of low resistance in the direction of movement, and does not generate vibration noise or contact with the wraps, and wear or burn marks on the wraps. Therefore, even if the rotational speed increases and the centrifugal force of the swinging scroll increases, or the differential pressure between the discharge pressure and the suction pressure increases, and the radial load acting on the pivoting axis increases, the pivoting axis displaces in the radial direction. Means are provided to prevent this.

In the present invention, a swing shaft eccentrically rotated to be supported by a rotation shaft, rotation prevention means for preventing rotation of the pivot shaft, and a pivot drive unit fitted to the pivot drive section of the pivot shaft and having swirl wraps on both sides. In a fluid machine having an actuating part constituted by combining a scroll and a pair of fixed scrolls fixed to one end of the casing, the pivot axis penetrates the actuating part and has a guide mechanism in the fixed scroll positioned at the outermost part. One end of the pivot shaft is guided to the guide mechanism and pivots to generate a load that cancels the radial load acting as the pivot shaft. This prevents the turning scroll from shifting or tilting beyond the set turning radius. The guide mechanism means an anti-rotation guide or a balance bearing attached to the outermost fixed scroll. The anti-rotation guide guides anti-rotation pins on two or more positions of the anti-rotation plate on the tip of the pivot shaft. Balance bearings guide the tip of the pivot.

According to the scroll fluid machine of the present invention, one end of the pivot shaft is guided by the guide mechanism to pivot, so that a radial load acts on the pivot shaft. The guide mechanism generates a load that dissipates the load acting in the radial direction of the pivot axis. As a result, it is possible to prevent the turning scroll from being displaced or inclined beyond the set turning radius. In addition, even when the scroll fluid machine is operated at a high speed and the centrifugal force of the turning scroll is large, the lap of the turning scroll and the lap of the fixed scroll do not come into contact with each other to generate vibration noise, wear, or leave burnt traces. . Therefore, a highly reliable scroll fluid machine can be provided.

In the swing drive mechanism, in the conventional structure, the tip of the swing drive shaft is displaced by the centrifugal force when rotating at high speed, the swing scroll wrap is in strong contact with the fixed scroll wrap, and the wrap is worn or cut, or noise is generated. Since this subject is solved by this invention, it can be miniaturized by making a scroll fluid machine a high speed rotation specification. Therefore, the present invention is likely to be used in a vacuum pump, a blower for a fuel cell, a compressor for a refrigerant, an air conditioner for a home and a package, an industrial air compressor, and the like, which should be miniaturized.

1 is an axial sectional view showing a first embodiment.
FIG. 2 is a cross-sectional view taken along line AA of FIG. 1.
3 is a partial sectional view showing a modification of the first embodiment.
4 is an axial cross-sectional view showing another modification of the first embodiment.
5 is an axial sectional view showing the second embodiment.
6 is a cross-sectional view taken along line AA of FIG. 5.
7 is an axial sectional view showing a modification of the second embodiment.
8 is an axial sectional view showing the third embodiment.
9 is an axial sectional view showing the fourth embodiment.
10 is an axial sectional view showing the fifth embodiment.
11 is an axial sectional view showing the sixth embodiment.
12 is an axial sectional view showing the seventh embodiment.
13 is an axial sectional view showing a modification of the seventh embodiment.
It is explanatory drawing of the scroll wrap combination state in FIG.
15 is an axial sectional view showing the eighth embodiment.
16 is an axial cross-sectional view showing a modification of the eighth embodiment.
17 is an axial sectional view showing the ninth embodiment.
18 is an axial sectional view showing the tenth embodiment.
19 is an axial sectional view showing a modification of the tenth embodiment.
20 is an axial sectional view showing a modification of the ninth or tenth embodiment.
21 is an axial sectional view showing the eleventh embodiment.
It is a partial sectional drawing which shows the 1st example of the coupling part of a swing scroll and a swing drive shaft.
It is a partial sectional view which shows the 2nd example of the coupling part of a swing scroll and a swing drive shaft.
24 is a partial cross-sectional view showing a third example of the engaging portion of the swing scroll and the swing drive shaft.
FIG. 25 is a partial cross-sectional view showing a portion of the anti-rotation bearing of the twelfth embodiment. FIG.
FIG. 26 is a partial sectional view showing a part of a balance bearing of the twelfth embodiment. FIG.
27 is an axial sectional view showing the thirteenth embodiment.

[1] First embodiment

1 shows a first embodiment. 2 is a cross-sectional view taken along the line A-A of FIG. The opposite surface of the lap of the first fixed scroll 1 having the spiral wrap is fixed to the hard plate of the casing 100. A pivoting scroll 10 is provided on the first fixed scroll 1 and has a swirl wrap on the hard board, and a second fixed scroll 2 is provided on the pivot scroll 10 and has a swirl wrap on the hard board. It is attached and fixed to the 1st fixed scroll 1. The 1st fixed scroll 1, the turning scroll 10, and the 2nd fixed scroll 2 comprise the operation part. A pair of 1st operating chambers 21 is comprised by combining the 1st fixed scroll wrap 1a and the swing scroll wrap 10a provided in the swing scroll 10. As shown in FIG. A pair of 2nd operation chamber 22 is comprised by combining the turning scroll wrap 10b provided in the turning scroll 10, and the 2nd fixed scroll wrap 2a.

The outer ring of the rotary bearing 101 is provided in the casing 100 at two places. The rotating shaft 102 is fitted to the inner ring of the rotary bearing 101. The stator 105 of the motor is fixed to the casing 100, and the motor rotor 106 is fixed to the rotating shaft 102. The rotating shaft 102 also has a balancer 47 for balancing the entire centrifugal force. The rotating shaft 102 is provided with bearing housings at both ends eccentrically from the rotation center, and the outer ring of the revolving bearing 103 is provided at the bearing housing. The pivot shaft 104 is fitted to the inner ring of the pivot bearing 103. The pivot shaft 104 penetrates through the first fixed scroll through hole 1c. A hole is provided in the center of the revolving scroll 10. The hole is fitted to the swing drive section 104a without rotation. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The anti-rotation plate 109 is fixed to one end of the pivot shaft 104b. As shown in FIG. 2, anti-rotation pins 110 are embedded in three inner surface sides of the anti-rotation plate 109. An anti-rotation bearing (guide mechanism) 111 is provided on the outside of the second fixed scroll 2 as an anti-rotation guide. The anti-rotation means is comprised by the anti-rotation board 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111. As shown in FIG. The anti-rotation pin 110 is combined in a state of being in contact with the anti-rotation bearing inner ring 112. If the outer diameter of the anti-rotation pin 110 is d1, the inner diameter of the anti-rotation bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. The following relationship is set between d1, D1, ε, and δ.

2ε-δ≤D1-d1≤2ε + δ (Equation 1)

If the value of D1-d1 is set in this way, the anti-rotation pin 110 will remain in contact with the anti-rotation bearing inner ring 112 substantially, and the rotation of the pivot shaft 104 will be reliably prevented. Moreover, the one end 104b of the pivot shaft does not bend inward with a strong force. Therefore, no noise is generated and the mechanical loss is small. Even if the centrifugal force of the revolving scroll 10 acts on the revolving drive part 104a, the revolving shaft one end 104b will not bend more than that when the internal gap of the bearing of the anti-rotation bearing (guide mechanism) 111 becomes zero. Thereby, the contact of the scroll wrap can be prevented. Therefore, the scroll fluid machine can rotate at a higher speed than before even if it has a large swing scroll.

The discharge cover 113 is fixed to the outer surface of the second fixed scroll 2 in a state of sealing the discharge chamber 114. The discharge cover 113 contains the anti-rotation plate 109 and the anti-rotation bearing (guide mechanism) 111. The discharge cover 113 is provided with a discharge port 108. A suction port 107 is provided on the outer circumferential portion of the second fixed scroll 2.

Next, the operation of the scroll fluid machine will be described. When a current flows through the coil of the stator 105, the rotor 106 rotates, the rotating shaft 102 rotates, and the rotating shaft 104 is prevented from rotating as described later, thereby driving eccentrically. The turning drive part 104a which is a part of the turning shaft 104 drives the turning scroll 10 to turn. The first operating chamber 21 composed of the first fixed scroll wrap 1a and the rotating scroll wrap 10a and the second operating chamber 22 composed of the second fixed scroll wrap 2a and the rotating scroll wrap 10b. ) Moves from the outer circumference side to the inner circumference, the volume decreases and the fluid inside is compressed. The pivotal plate communication hole 10c is provided in the hard-plate center part of the pivoting scroll 10. As shown in FIG. Therefore, the operation chamber 21 and the operation chamber 22 communicate with each other at the center part. As a result, the fluid is sucked in the suction port 107, compressed through the suction chamber 130, joined to the operation chamber 22, and passed to the discharge chamber 114 through the second fixed scroll through hole 2c. It flows in and is discharged from the discharge port 108 to the outside.

Since there is a relationship between the outer diameter d1 of the anti-rotation pin 110 and the inner diameter D1 of the anti-rotation bearing inner ring 112 and the turning radius ε, the anti-rotation pin 110 is always the anti-rotation bearing inner ring 112. The pivoting motion is maintained while maintaining a certain contact force between the teeth. Since the anti-rotation plate 109 is located at two or more positions of the anti-rotation plate 109, the anti-rotation plate 109 rotates but cannot rotate. Since the anti-rotation plate 109 is fixed to one end of the pivot shaft 104b, the pivot shaft 104 is pivotally prevented from rotating. Moreover, since the turning scroll 10 is fitted in the state which does not rotate relative to the turning drive part 104a, rotating rotation is prevented and it rotates.

However, since the swinging scroll 10 has a mass, centrifugal force is generated in the direction perpendicular to the axis when the swinging movement is performed. The entire centrifugal force is dissipated by the balancer 47. However, the centrifugal force is a load that tries to displace the orbiting scroll in the radial direction. This load is a load to bend the swing drive part 104a. The swing drive part 104a squeezes the slewing bearing 103 in the direction of the combined load. As a result, the turning scroll 10 is also displaced while tilting in the direction of the combined load. For this reason, the turning scroll wraps 10a and 10b are close to the first fixed scroll wrap 1a and the second fixed scroll wrap 2a. If the wraps are too close to each other, the gap between the wraps, which were originally set small, becomes 0 in order to reduce leakage, and the sliding starts. This causes sliding losses in the lap. In addition, vibration noise is generated in the scroll fluid machine. In addition, the wear of the lap may progress, or the lap may burn. That is, the performance and reliability of the scroll fluid machine are compromised.

However, according to the present invention, since the anti-rotation pin 110 is in contact with the anti-rotation bearing inner ring 112, the pivot shaft one end 104b is determined by the anti-rotation pin 110 and the anti-rotation bearing inner ring 112. It cannot be displaced beyond the turning radius. Therefore, even if the turning scroll 10 rotates at a high speed and the centrifugal force is increased to increase the load for bending the turning drive part 104a, the bending drive part 104a is prevented from bending. Therefore, the wraps do not touch each other. Therefore, the scroll fluid machine of the present invention can realize a higher speed rotation than the prior art even with a large swing scroll.

3 is a partial sectional view showing a modification of the first embodiment. As shown in FIG. 3, the anti-rotation sliding member (guide mechanism) 115 is used instead of the anti-rotation bearing (guide mechanism) 111 as the anti-rotation guide. The anti-rotation means is comprised by the anti-rotation board 109, anti-rotation pin 110, and anti-rotation sliding member (guide mechanism) 115. As shown in FIG. The anti-rotation sliding member (guide mechanism) 115 is made of a self-lubricating component such as resin. Since the anti-rotation pin 110 is guided and pivots while being inscribed on the inner surface of the anti-rotation sliding member (guide mechanism) 115, rotation of the pivot axis 104 and the pivoting scroll 10 is prevented and the pivot axis One end 104b cannot be displaced beyond the turning radius determined by the anti-rotation pin 110 and the anti-rotation sliding member (guide mechanism) 115.

In this case, since the anti-rotation pin 110 and the anti-rotation sliding member (guide mechanism) 115 contact each other, the rotation of the turning scroll is reliably prevented. Moreover, even if the centrifugal force of the revolving scroll 10 acts on the revolving drive part 104a, the revolving shaft one end 104b is bent after the revolving pin 110 and the revolving anti-sliding member (guide mechanism) 115 are in contact with each other. Do not. As a result, contact between the laps can be prevented. Therefore, the scroll fluid machine according to the present invention can perform a high-precision turning motion at a higher speed than before even if it has a large turning scroll.

4 shows another modification of the first embodiment. 4 shows an example in which a fan 31 is provided at the rear end 102a of the rotating shaft and cooled when the first embodiment is applied to a vacuum pump. A bearing hole 35 is provided with a penetrating vent 36. The exhaust port 34 is provided on the side of the casing 100 closer to the first fixed scroll 1 than the stator 105. The pivot shaft 104 is provided with a penetrating pivot shaft passage 32. The bottom plate 100a of the casing 100 is drilled with a filter 30. When the fan 31 rotates together with the rotation shaft 102, air enters from the outside through the filter 30. The air which entered the filter 30 ventilates the motor part space 33 in the casing 100 through the vent 36, and is discharged | emitted from the exhaust port 34 to the outside. In the meantime, the rotary bearing 101 and the stator 105 are cooled, and excessive temperature rise is prevented. In addition, the air entering the filter 30 exits the fan 31 and flows into the discharge chamber 114 through the rotary shaft vent 32, and the first operating chamber 21 and the second operating chamber 22 are used. Along with the air discharged from the discharge port 108 is discharged to the outside. In the meantime, the center part of the turning bearing 101 and the turning scroll 10 is cooled, and excessive temperature rise is prevented.

FIG. 4 also shows an example in which a seal component is provided to seal the space between the operating chamber side and the casing side when the first embodiment of the present invention is applied to a vacuum pump. The ring shaped inner surface seal 42 hangs around the first fixed scroll through hole 1c. The seal plate 40 rests on the pivot shaft 104 by bringing it into contact with the inner seal 42. The seal cover 41 rests on the casing side facing the seal plate 40. The ring-shaped outer seal 43 depends on the seal cover 41 and is in contact with the seal plate 40. With this configuration, the space on the operating chamber side and the casing side are sealed in two layers with the first fixed scroll through hole 1c interposed therebetween. This reliably prevents gas from the operating chamber from leaking into the casing. In addition, the gas to be discharged is cut off from the outside air by the discharge cover 113, and is discharged through an external pipe not shown connected to the discharge port 108. Therefore, even if toxic gas or corrosive gas flows into the working chamber, it does not leak out to the outside air.

[2] Embodiment 2

5 shows a second embodiment. 6 is a cross-sectional view taken along the line A-A of FIG. The same components as those in the first embodiment use the same symbols and names, and descriptions thereof are omitted. The discharge cover 113 rests on the outer surface of the hard plate of the second fixed scroll 2. The balance bearing (guide mechanism) 51 rests inside the discharge cover 113. The outer circumferential surface of the pivot shaft one end 104b pivots while inscribed in the balance bearing inner ring 52. If the outer diameter of one end of the pivot shaft 104b is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the pivot shaft 104 when the scroll fluid machine is operated is ε, and the inner gap of the bearing is δ. , d2, D2, ε, and δ are set to have the following relationship.

2ε-δ≤D2-d2≤2ε + δ (Equation 2)

When the value of D1-d1 is set in this way, the one end 104b of the pivot shaft maintains a state of almost contacting the balance bearing inner ring 52. Moreover, the one end 104b of the pivot shaft does not bend inward with a strong force. Therefore, no noise is generated, and the mechanical loss is small. Even if the centrifugal force of the revolving scroll 10 acts on the revolving drive part 104a, the revolving shaft one end 104b will not bend more than that when the internal gap of the bearing of the balance bearing (guide mechanism) 51 becomes zero. Thereby, the contact of the scroll wrap can be prevented. Therefore, the scroll fluid machine can rotate at a higher speed than before even if it has a large swing scroll.

The anti-rotation plate 60 is fixed to the other end 104c of the pivot shaft. The anti-rotation pin 61 is embedded in two or more places of the anti-rotation board 60. The anti-rotation bearing 62 depends on the base plate 100a of the casing 100. The anti-rotation pin 61 pivots while being inscribed to the anti-rotation bearing inner ring 63. If the outer diameter of the anti-rotation pin 61 is d3, the inner diameter of the anti-rotation bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. The following relationship is set between d3, D3, ε, and δ.

2ε-δ≤D3-d3≤2ε + δ (Equation 3)

When the value of D1-d1 is set in this way, the anti-rotation pin 61 maintains a state of almost contacting the anti-rotation bearing inner ring 63. Therefore, the rotation of the swing scroll 10 is surely prevented. Further, the other end 104c of the pivot shaft is not bent inward with a strong force. Therefore, no noise is generated, and the mechanical loss is small.

7 shows a modification of the second embodiment. As shown in FIG. 7, one end 104b of the pivot shaft has a jar shape having a curved surface in the axial direction. This ensures that one end of the pivot shaft 104b is free from contact with the balance bearing inner ring 52 (Misaligned contact). Therefore, shaving and abrasion are hardly generated on the surface where the pivot shaft one end 104b and the balance bearing inner ring 52 contact. Therefore, the reliability of the scroll fluid machine is high. In addition, the anti-rotation sliding member 64 is used as a guide of the anti-rotation pin 61 provided on the anti-rotation plate 60. The anti-rotation sliding member 64 is made of a self-lubricating member such as resin. The anti-rotation sliding member 64 may be made of a metal member having a wear resistant surface treatment.

[3] Third Embodiment

8 shows a third embodiment. The cover 70 seals the outer surface of the central portion of the second fixed scroll 2 and blocks the operation chamber side and the atmosphere side. The discharge port 71 is provided below the stator 105 on the outer circumference of the casing 100. Fluid flows into the inlet 107 and is compressed in the first operating chamber 21 and the second operating chamber 22 to enter the casing 100 at the first fixed scroll through-hole 1c and into the casing. It passes through the inside of the 100 and is discharged to the outside from the discharge port 71. According to this structure, the simple cover 70 is solved instead of the discharge cover 113. This reduces the number of machined parts of the scroll fluid machine and reduces the cost. In addition, since the projections are eliminated, the overall length can be shortened, and the inside of the casing can be cooled by the movement of the working fluid.

[4] fourth embodiment

9 shows a fourth embodiment. The fluid machine shown in FIG. 9 is a twin scroll fluid machine having scrolls at both ends of the pivot axis 104. On the right side of the casing 100, the lap opposite surface of the first fixed scroll 1 is fixed. Overlaid on the first fixed scroll 1, the first turning scroll 11 is provided. A second fixed scroll 2 is provided on the first swing scroll 11 and is fixed to the first fixed scroll 1. The 1st fixed scroll 1, the 1st rotation scroll 11, and the 2nd fixed scroll 2 comprise the operation part of one end of a pivot axis. The first fixed scroll wrap 1a and the first swing scroll wrap 11a are combined to form a pair of first operating chambers 21. A pair of 2nd operation chamber 22 is comprised by combining the 1st turning scroll wrap 11b and the 2nd fixed scroll wrap 2a. The 1st turning hard board communication port 11c is provided in the hard board center part of the 1st turning scroll 11. As a result, the first operating chamber 21 joins the second operating chamber 22 through the first swing hard plate communication port 11c. As a result, the fluid is sucked in the first suction port 107a, compressed through the first suction chamber 131, joined to the operation chamber 22, and the first through the second fixed scroll through hole 2c. It flows into the 1st discharge chamber 114a in the discharge cover 113a, and is discharged from the 1st discharge port 108a to the outside.

On the left side of the casing 100, a wrap opposite surface of the third fixed scroll 3 is fixed. The second pivoting scroll 12 is provided on the third fixed scroll 3. The fourth fixed scroll 4 is provided on the second swing scroll 12 and is fixed to the third fixed scroll 3. The third fixed scroll 3, the second swing scroll 12, and the fourth fixed scroll 4 constitute an operating part on the other end of the pivot axis. The third fixed scroll wrap 3a and the second swing scroll wrap 12a are combined to form a pair of third operating chambers 23. The second swing scroll wrap 12b and the fourth fixed scroll wrap 4a are combined to form a pair of fourth operating chambers 24. The rotary shaft 102 rotates, and the pivot shaft 104 is prevented from rotating so that the pivot shaft 104 is eccentrically driven. The second swing driver 104d, which is part of the swing shaft 104, drives the swing scroll 12 to swing. The working fluid moves from the outer circumferential side to the inner circumferential side of the third operating chamber 23 and the fourth operating chamber 24, and the volume decreases and is compressed. The 2nd turning hard board communication port 12c is provided in the hard board center part of the 2nd turning scroll 12. As shown in FIG. As a result, the third operating chamber 23 joins the fourth operating chamber 24 through the second pivotal plate communication port 12c. As a result, the working fluid sucked in the second suction port 107b is compressed via the second suction chamber 132, through the fourth fixed scroll through hole 4c, and the first fluid in the second discharge cover 113b. It flows into the 2 discharge chamber 114b, and is discharged | emitted outside from the 2nd discharge port 108b.

The outer ring of the rotary bearing 101 is provided in the casing 100 at two places. The rotating shaft 102 is fitted to the inner ring of the rotary bearing 101. The rotating shaft 102 has two balancers 47 for balancing the entire centrifugal force. The stator 105 of the motor is fixed to the casing 100, and the rotor 106 of the motor is fixed to the rotating shaft 102. The rotating shaft 102 also has a balancer 47 for balancing the entire centrifugal force. The rotating shaft 102 is provided with bearing housings at both ends eccentrically from the rotation center, and the outer ring of the revolving bearing 103 is provided in the bearing housing. The pivot shaft 104 is fitted to the inner ring of the pivot bearing 103. The pivot shaft 104 penetrates through the first fixed scroll through hole 1c. A hole is provided in the center of the 1st turning scroll 11. The hole is fitted to the swing drive section 104a without rotation. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The anti-rotation plate 109 is fixed to one end 104b of the pivot shaft. As shown in FIG. 2, the anti-rotation pin 110 is embedded in three places on the inner surface side of the anti-rotation plate 109. The anti-rotation bearing (guide mechanism) 111 is provided on the outside of the second fixed scroll 2. The anti-rotation pin 110 is combined in a state of being in contact with the anti-rotation bearing inner ring 112. If the outer diameter of the anti-rotation pin 110 is d1, the inner diameter of the anti-rotation bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. d1, D1, ε, and δ are set to have a relationship with Equation 1.

The pivot shaft 104 penetrates through the third fixed scroll through hole 3c. A hole is provided in the center of the second swing scroll 12. The hole is fitted to the second swing drive section 104d without being rotated relative to it. The pivot shaft other end 104c penetrates through the fourth fixed scroll through hole 4c and extends outward. The bearing block 50 rests on the outer side of the hard plate of the fourth fixed scroll 4. The balance bearing (guide mechanism) 51 rests inside the bearing block 50. The outer circumferential surface of the other end 104c of the pivot shaft pivots while being inscribed with the balance bearing inner ring 52. If the outer diameter of the pivot shaft other end 104c is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing inner clearance is δ. d2, D2, ε, and δ are set to have a relationship of Equation 2.

In the present embodiment, as described above, a pair of scroll parts are provided on one side of the casing 100, and a pair of scroll parts are also provided on the opposite side of the casing 100. Therefore, in the present embodiment, the flow rate can be twice that of the fluid machine provided with one pair of scroll units on one side of the casing 100. The antirotation mechanism is provided at one end 104b of the pivot shaft on the right side of the pivot shaft 104. In addition, there is a relationship of expression 1 between the outer diameter of the anti-rotation pin 110 and the inner diameter of the inner ring 112 of the anti-rotation bearing. Therefore, the rotation of the pivot shaft 104 is reliably prevented. In addition, bending of one end 104b of the pivot shaft due to centrifugal force is prevented. The outer circumferential surface of the pivot shaft other end 104c pivots while inscribed in the balance bearing inner ring 52. In addition, there is a relationship of the expression (2) between the pivot shaft other end 104c and the balance bearing inner ring 52. Therefore, the bending of the other end 104c of the pivot shaft by centrifugal force is prevented.

[5] Fifth Embodiment

10 shows a fifth embodiment. The structure of the drive portion is the same as in the fourth embodiment. The same components as those in the fourth embodiment use the same symbols and names, and descriptions thereof are omitted. This embodiment is different from the fourth embodiment. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The first discharge cover 113a rests on the outer surface of the hard plate of the second fixed scroll 2. The first balance bearing (guiding mechanism) 51a rests inside the first discharge cover 113a. The outer circumferential surface of one end of the pivot shaft 104b pivots while inscribed in the first balance bearing inner ring 52a. The outer diameter of one end of the pivot shaft 104b is d2, the inner diameter of the first balance bearing inner ring 52a is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing inner clearance is δ. If so, d2, D2, ε, and δ are set to be in the relation of Equation 2.

The second discharge cover 113b rests on the outer surface of the hard plate of the fourth fixed scroll 4. The second balance bearing (guiding mechanism) 51b rests inside the second discharge cover 113b. The outer circumferential surface of the pivot shaft other end 104c pivots while inscribed in the second balance bearing inner ring 52b. The outer diameter of the pivot shaft other end 104c is d2, the inner diameter of the second balance bearing inner ring 52b is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing inner clearance is δ. If so, d2, D2, ε, and δ are set to be in the relation of Equation 2.

The anti-rotation plate 60 rests relatively between the right side of the swing bearing 103 and the hard plate of the first fixed scroll 1. The anti-rotation pin 61 is embedded in three places of the outer peripheral part of the anti-rotation board. The anti-rotation bearing 62 is attached to the hard plate of the first fixed scroll 1. The anti-rotation pin 61 pivots while being inscribed to the anti-rotation bearing inner ring 63. If the outer diameter of the anti-rotation pin 61 is d3, the inner diameter of the anti-rotation bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. d3, D3, ε, and δ are set to have a relationship with Equation 3.

In the present embodiment, as described above, one pair of scroll sections is provided on one side of the casing 100, and one pair of scroll sections is provided on the other side of the casing 100. Therefore, this embodiment can produce twice the flow rate of the fluid machine provided with one pair of scroll units on one side of the casing 100 as in the fourth embodiment of the present invention. The outer circumferential surface of one end of the pivot shaft 104b pivots while inscribed in the first balance bearing inner ring 52a. There is a relation of expression 2 between the pivot end 104b and the first balance bearing inner ring 52a. Therefore, bending of one end 104b of the pivot shaft by centrifugal force is prevented. The outer circumferential surface of the other end 104c of the pivot shaft pivots while inscribed in the second balance bearing inner ring 52b. There is also a relation of expression 2 between the pivot shaft other end 104c and the second balance bearing inner ring 52b. Therefore, the bending of the other end 104c of the pivot shaft by centrifugal force is prevented.

[6] Sixth embodiment

11 shows a sixth embodiment. The outer surface of the center portion of the second fixed scroll 2 is covered with the first cover 70a, and the operation chamber side and the atmosphere side are blocked. In addition, the outer surface of the central portion of the fourth fixed scroll 4 is covered with a second cover 70b to block the operation chamber side and the atmospheric side. In addition, a discharge port 71 is provided in a part of the side surface of the casing 100. Fluid exiting the first operating chamber 21 and the second operating chamber 22 enters the casing 100 at the first fixed scroll through hole 1c. The fluid exiting the third operating chamber 23 and the fourth operating chamber 24 enters the casing 100 from the third through hole 3c. Fluid entering the casing 100 passes through the inside of the casing 100 and is discharged to the outside from the discharge port 71. In this structure, since it ends with a simple first cover 70a and a second cover 70b as shown in FIG. 11, the first discharge cover 113a and the second discharge cover 113b as shown in FIG. You do not have to use. Therefore, in this structure, two machining parts can be reduced, cost can be reduced, and projections can be eliminated, so that the overall length can be shortened. It is also possible to cool the inside of the casing with compressed working fluid.

[7] Seventh embodiment

12 shows a seventh embodiment. 12 shows a fluid machine having two pairs of scroll portions in the pivot drive 104a. The same components as those in the first embodiment use the same symbols and names, and descriptions thereof are omitted. The opposite surface of the wrap of the first fixed scroll 1 is fixed to the casing 100. The first turning scroll 11 is superimposed on the first fixed scroll 1. The third fixed scroll 3 is superimposed on the first swing scroll 11 and is fixed to the first fixed scroll 1. The 2nd turning scroll 12 is superimposed on the 3rd fixed scroll 3, and is provided. The second fixed scroll 2 is superimposed on the second pivoting scroll 12 and is fixed to the first fixed scroll 1 together with the third fixed scroll 3. The first fixed scroll 1, the first swing scroll 11, the third fixed scroll 3, the second swing scroll 12 and the second fixed scroll 2 constitute an operation unit. The pair of first operating chambers 21 is constituted by a combination of the first fixed scroll wrap 1a and the first swing scroll wrap 11a. The pair of second operating chambers 22 is constituted by the combination of the first swing scroll wrap 11b and the third fixed scroll wrap 3a. The pair of third operating chambers 23 is constituted by a combination of the third fixed scroll wrap 3b and the second swing scroll wrap 12a. The pair of fourth operating chambers 24 is constituted by the combination of the second swing scroll wrap 12b and the second fixed scroll wrap 2a. Since the 3rd fixed scroll suction communication port 3d is provided in the 3rd fixed scroll 3, the 1st suction chamber 131 and the 2nd suction chamber 132 are connected. The 1st turning hard board communication port 11c is provided in the hard board center part of the 1st turning scroll 11. As a result, the first operating chamber 21 joins the second operating chamber 22 through the first swing hard plate communication port 11c. The 2nd turning hard board communication port 12c is provided in the hard board center part of the 2nd turning scroll 12. As shown in FIG. As a result, the third operating chamber 23 joins the fourth operating chamber 24 through the second pivoting plate communication hole 12c. Accordingly, the fluid is sucked into all the operating chambers at the suction port 107 and discharged to the outside at the discharge port 108.

The pivot shaft 104 penetrates through the first fixed scroll through hole 1c. A hole is provided in the center of the first swing scroll 11. The hole is fitted to the swing drive section 104a without rotation. The pivot shaft 104 penetrates through the third fixed scroll through hole 3c. Holes are also provided in the center of the second swing scroll 12. The hole is fitted to the swing drive section 104a without rotation. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The discharge cover 113 hangs on the outer surface of the hard plate of the second fixed scroll 2. A balance bearing (guide mechanism) 51 rests inside the bearing discharge cover 113. The outer circumferential surface of the pivot shaft one end 104b pivots while inscribed in the balance bearing inner ring 52. If the outer diameter of the pivot shaft one end 104b is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing inner clearance is δ. The equation 2 relationship is set between d2, D2, ε, and δ. The same rotation preventing mechanism as that of the second embodiment is provided at the other end 104c of the pivot shaft. The anti-rotation bearing 62 is attached to the bottom plate 100a. The anti-rotation pin 61 maintains a state of almost contacting the anti-rotation bearing inner ring 63. Therefore, the rotation of the pivot shaft 104 is reliably prevented.

According to the present embodiment, the pivot shaft one end 104b and the balance bearing inner ring 52 remain in contact with each other. As a result, even if the centrifugal force of the first swing scroll 11 and the second swing scroll 12 acts on the swing drive section 104a, the one end 104b of the swing shaft has a zero bearing internal clearance of the balance bearing inner ring 52. No more is bent. Therefore, the contact between the wraps is prevented. Further, even if the scroll fluid machine has a large swing scroll, it can rotate at a higher speed than before. In addition, the flow rate of twice the fluid machine provided with one pair of scroll sections on one side of the casing 100 can be achieved.

13 and 14 show an example in which the phases of suction and discharge are shifted (shifted) in the seventh embodiment. The scroll fluid machine can change the phase of suction and discharge with respect to the eccentric direction of the pivot axis by changing the rotational position of the lap when mounting. As shown in Fig. 14, the first fixed scroll wrap 1a and the first turning scroll wrap 11a, the third fixed scroll wrap 3a and the first turning scroll wrap 11b, and the third fixed scroll wrap 3b ), The second swing scroll wrap 12a, the second fixed scroll wrap 2a, and the second swing scroll wrap 12b are each rotated by 90 degrees. Therefore, the first turning scroll wrap 11a, the first turning scroll wrap 11b, the second turning scroll wrap 12a, and the second turning scroll wrap 12b are all in the same direction (the right side of the paper in the drawing). Despite being eccentric, the phases of the four operating chambers are off by 90 degrees.

[8] Eighth Embodiment

15 shows an eighth embodiment. The same components as those in the first embodiment use the same symbols and names, and descriptions thereof are omitted. The opposite surface of the wrap of the first fixed scroll 1 is fixed to the right side of the casing 100. The first turning scroll 11 is superimposed on the first fixed scroll 1. The third fixed scroll 3 is superimposed on the first swing scroll 11 and is fixed to the first fixed scroll 1. The 2nd turning scroll 12 is superimposed on the 3rd fixed scroll 3, and is provided. The second fixed scroll 2 is superimposed on the second pivoting scroll 12 and is fixed to the first fixed scroll 1 together with the third fixed scroll 3. The first fixed scroll 1, the first swing scroll 11, the third fixed scroll 3, the second swing scroll 12 and the second fixed scroll 2 constitute an operation part at one end of the pivot axis. . The pair of first operating chambers 21 is constituted by a combination of the first fixed scroll wrap 1a and the first swing scroll wrap 11a. The pair of second operating chambers 22 is constituted by the combination of the first swing scroll wrap 11b and the third fixed scroll wrap 3a. The 1st turning hard board communication port 11c is provided in the hard board center part of the 1st turning scroll 11. The first operating chamber 21 joins the second operating chamber 22 through the first pivotal hard plate communicating port 11c. The pair of third operating chambers 23 is constituted by a combination of the third fixed scroll wrap 3b and the second swing scroll wrap 12a. The pair of fourth operating chambers 24 is constituted by the combination of the second swing scroll wrap 12b and the second fixed scroll wrap 2a. The 2nd turning hard board communication port 12c is provided in the hard board center part of the 2nd turning scroll 12. As shown in FIG. The third operation chamber 23 joins the fourth operation chamber 24 through the second pivoting plate communication hole 12c. Since the 3rd fixed scroll suction communication port 3d is provided in the 3rd fixed scroll 3, the 1st suction chamber 131 and the 2nd suction chamber 132 are in communication. In addition, since the third fixed scroll through hole 3c is provided at the center of the third fixed scroll 3, the fluid sucked in the first suction port 107a is compressed in the operating chambers 21, 22, 23, 24. Then, it aggregates into the discharge chamber 114 in the 1st discharge cover 113a, and is discharged to the exterior from the 1st discharge port 108a.

The opposite surface of the wrap of the fourth fixed scroll 4 is fixed to the left side of the casing 100. The third turning scroll 13 is superimposed on the fourth fixed scroll 4. The sixth fixed scroll 6 is superimposed on the third turning scroll 13 and fixed to the fourth fixed scroll 4. The fourth pivoting scroll 14 is superimposed on the sixth fixed scroll 6. The fifth fixed scroll 5 is superimposed on the fourth swing scroll 14 and fixed to the fourth fixed scroll 4 together with the sixth fixed scroll 6. The fourth fixed scroll 4, the third rotating scroll 13, the sixth fixed scroll 6, the fourth rotating scroll 14 and the fifth fixed scroll 5 constitute an operating part on the other end of the pivot axis. . The pair of fifth operating chambers 25 is constituted by the combination of the fourth fixed scroll wrap 4a and the third swing scroll wrap 13a. The pair of sixth operating chambers 26 is constituted by the combination of the third swing scroll wrap 13b and the sixth fixed scroll wrap 6a. The third pivotal plate communication port 13c is provided at the middle of the solid plate of the third pivoting scroll 13. The fifth operation chamber 25 joins the sixth operation chamber 26 through the third pivoting plate communication port 13c. The pair of seventh operating chambers 27 is constituted by the combination of the sixth fixed scroll wrap 6b and the fourth swing scroll wrap 14a. The pair of eighth operating chambers 28 is constituted by the combination of the fourth swing scroll wrap 14b and the fifth fixed scroll wrap 5a. The fourth swing plate communication hole 14c is provided at the center of the plate of the fourth swing scroll 14. As a result, the seventh operation chamber 27 joins the eighth operation chamber 28 through the fourth pivoting hard plate communication port 14c. Since the sixth fixed scroll suction communication port 6d is provided in the sixth fixed scroll 6, the third suction chamber 133 and the fourth suction chamber 134 communicate with each other. In addition, since the sixth fixed scroll through hole 6c is provided at the center portion of the sixth fixed scroll 6, the fluid sucked in the second suction port 107b is compressed in the operating chambers 25, 26, 27, 28. And is discharged to the outside from the second discharge port 108b provided in the second discharge cover 113b.

The structure of the drive portion is the same as in the first embodiment. The pivot shaft 104 penetrates through the first fixed scroll through hole 1c. Holes are provided in the centers of the first swing scroll 11 and the second swing scroll 12. The hole is fitted to the swing drive section 104a without rotation. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The anti-rotation plate 109 is fixed to one end 104b of the pivot shaft. As shown in FIG. 2, the anti-rotation pin 110 is embedded in three places on the inner surface side of the anti-rotation plate 109. An anti-rotation bearing (guide mechanism) 111 is provided on the outside of the second fixed scroll 2 as the anti-rotation guide. The anti-rotation means is comprised by the anti-rotation board 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111. As shown in FIG. The anti-rotation pin 110 is fitted in contact with the anti-rotation bearing inner ring 112. If the outer diameter of the anti-rotation pin 110 is d1, the inner diameter of the anti-rotation bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. d1, D1, ε, and δ are set to have a relationship with Equation 1.

The pivot shaft 104 penetrates through the fourth fixed scroll through hole 4c. Holes are provided in the centers of the third swing scroll 13 and the fourth swing scroll 14. The hole is fitted to the second swing drive section 104d in a state in which it does not rotate relatively. The pivot shaft other end 104c penetrates through the fifth fixed scroll through hole 5c and extends outward. The second discharge cover 113b rests on the outer surface of the hard plate of the fifth fixed scroll 5. A balance bearing (guide mechanism) 51 rests inside the second discharge cover 113b. The outer circumferential surface of the pivot shaft other end 104c pivots while inscribed in the balance bearing inner ring 52. If the outer diameter of the pivot shaft other end 104c is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing inner clearance is δ. d2, D2, ε, and δ are set to have a relationship of Equation 2.

In this embodiment, since the configuration is as described above, four times the flow rate of the fluid machine provided with one pair of scroll units on one side of the casing 100 can be achieved. The rotation of the pivot shaft 104 is reliably prevented by the rotation prevention means provided in the pivot shaft one end 104b on the right side of the pivot shaft 104. In addition, bending of one end 104b of the pivot shaft due to centrifugal force is prevented. The outer circumferential surface of the pivot shaft other end 104c pivots while inscribed in the balance bearing inner ring 52. There is a relationship of expression (2) between the pivot shaft other end 104c and the balance bearing inner ring 52. Therefore, the bending of the other end 104c of the pivot shaft by centrifugal force is prevented.

16 shows a modification of the eighth embodiment. The structure of the drive portion is the same as in the eighth embodiment. In the present embodiment, the same parts as those in the eighth embodiment use the same symbols and names, and descriptions thereof are omitted. The difference between the present embodiment and the eighth embodiment will be described. One end of the pivot shaft 104b penetrates through the second fixed scroll through hole 2c and extends outward. The first discharge cover 113a rests on the outer surface of the hard plate of the second fixed scroll 2. The first balance bearing (guiding mechanism) 51a rests inside the first discharge cover 113a. The outer circumferential surface of one end 104b of the pivot shaft pivots while inscribed in the balance bearing inner ring 52a. If the outer diameter of one end of the pivot shaft 104b is d2, the inner diameter of the balance bearing inner ring 52a is D2, the turning radius of the pivot shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. d2, D2, ε, and δ are set to be in the relation of Equation 2. Therefore, bending of one end 104b of the pivot shaft by centrifugal force is prevented. The pivot shaft other end 104c penetrates through the fifth fixed scroll through hole 5c and extends outward. The second discharge cover 113b hangs on the outer surface of the hard plate of the second fixed scroll 2. The second balance bearing (guiding mechanism) 51b rests inside the second discharge cover 113b. The outer circumferential surface of the pivot shaft other end 104c pivots while inscribed in the second balance bearing inner ring 52b. There is also a relation of expression 2 between the pivot shaft other end 104c and the second balance bearing inner ring 52b. Therefore, the bending by the centrifugal force of the other end 104c of the pivot shaft is prevented.

The anti-rotation plate 60 rests relatively between the right side of the swing bearing 103 and the hard plate of the first fixed scroll 1. The anti-rotation pin 61 is embedded in three places of the outer peripheral part of the anti-rotation board 60. The anti-rotation bearing 62 is attached to the hard plate of the first fixed scroll 1. The anti-rotation means is comprised by the anti-rotation board 60, the anti-rotation pin 61, and the anti-rotation bearing 62. As shown in FIG. The anti-rotation pin 61 pivots while being inscribed to the anti-rotation bearing inner ring 63. If the outer diameter of the anti-rotation pin 61 is d3, the inner diameter of the anti-rotation bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. d3, D3, ε, and δ are set to have a relationship with Equation 3.

In this embodiment, since the configuration is as described above, as in the eighth embodiment of the present invention, a flow rate four times as high as that of the fluid machine provided with one pair of scroll units on one side of the casing 100 can be obtained.

[9] Ninth Embodiment

17 shows a ninth embodiment. The same components as those in the seventh embodiment use the same symbols and names, and descriptions thereof are omitted. The third fixed scroll 3 is divided into two. The third fixed scroll first hard plate 3e and the third fixed scroll second hard plate 3f are brought into close contact with each other and are integrated. The space is provided in the center part of 3rd fixed scroll 1st hard board 3e and 3rd fixed scroll 2nd hard board 3f. In this space, the seal plate 44 fixed to the swing drive section 104a is slidably fitted. The first seal 45 attached to the third fixed scroll first hard plate 3e and the second seal 46 attached to the third fixed scroll second hard plate 3f are formed on both sides of the seal plate 44. I seal it. The third fixed scroll through hole 3c is blocked by the seal in the middle.

The first operating chamber 21 and the second operating chamber 22 are formed by a combination of the first fixed scroll wrap 1a, the first turning scroll wrap 11a, 11b, and the third fixed scroll wrap 3a. It consists. In addition, the third operating chamber 23 and the fourth operating chamber 24 by the combination of the third fixed scroll wrap 3b, the second turning scroll wrap 12a, 12b, and the second fixed scroll wrap 2a are provided. It constitutes an inflator.

The inlet 207b is provided in the discharge cover 113 provided in the 2nd fixed scroll 2, and a working fluid flows in. The working fluid enters the center of the fourth operating chamber 24 at the second fixed scroll through hole 2c, enters the third operating chamber 23 at the second pivoting plate communication hole 12c, and enters the outer periphery. Inflates while moving towards The working fluid then gives a turning force to the second turning scroll 12. An inflator outlet 208b is provided on the outer periphery of the second fixed scroll 2. The expanded working fluid is discharged from the inflator outlet 208b. The compressor suction port 207a is provided in the outer peripheral portion of the first fixed scroll 1. The inlet of the cooler (water heater) 121 is connected to the inflator outlet 208b, and the outlet is connected to the compressor inlet 207a. The working fluid cooled by the cooler 121 and brought to a low temperature enters the first operating chamber 21 and the second operating chamber 22 at the compressor suction port 207a and is compressed while moving toward the inner circumference. The compressed working fluid is joined by the first pivotal plate communication hole 11c, enters the casing 100 at the first fixed scroll through hole 1c, and is discharged to the outside from the compressor discharge port 208a. The inlet of the heater (collector) 120 is connected to the compressor discharge port 208a, and the outlet is connected to the expander inlet 207b. The working fluid exiting the compressor discharge port 208a is heated by the heater 120 to become a high temperature and flows into the expander at the expander inlet 207b. In this stroke, the work amount of the expander is larger than the power of the compressor, and the expander drives the compressor. The inflator further drives the pivot drive section 104a and eccentrically drives the pivot shaft 104. The pivot shaft 104 rotates the rotation shaft 102. The rotary shaft 102 rotates the mounted rotor 105 to generate electromotive force in the coil of the stator 106. As a result, electric power can be obtained from the coil. The fluid machine becomes a generator.

In general, when driving a compressor with an expander, the power is transmitted by the rotational force, so a loss occurs in the bearings supporting the respective drive shafts. However, in the present embodiment, since the expander and the compressor are mounted on the same swing driver 104a, power is transmitted as a load, so that no loss occurs between the expander and the compressor. On the other hand, the working fluid is preferably a stable gas that does not liquefy at room temperature, such as air or nitrogen or helium.

[10] Tenth Embodiment

18 shows a tenth embodiment. This embodiment shows an example in which a scroll fluid machine similar to the ninth embodiment is applied to a fuel cell system using two pairs of four pairs of operating chambers as an expander and two other pairs as blowers.

A blower suction port 307 is provided at the outer circumferential portion of the first fixed scroll 1. Air enters the first operating chamber 21 and the second operating chamber 22 at the blower inlet 307 and is compressed while moving toward the inner circumference. The compressed air enters into the casing 100 at the first fixed scroll through hole 1c and is discharged to the outside from the blower discharge port 308. An inflator inlet 207b is provided in the center of the second fixed scroll 2. The inlet of the fuel cell 122 is connected to the blower discharge port 308, and the outlet is connected to the expander inlet 207b. The exhaust air exiting the fuel cell 122 still maintains a high pressure to some extent, and enters the center of the third operating chamber 23 and the fourth operating chamber 24 from the second fixed scroll through hole 2c. It expands as it moves toward (外 周). At this time, the air gives a turning force to the second turning scroll 12. An inflator outlet 208b is provided on the outer periphery of the second fixed scroll 2. The expanded air is discharged from the inflator outlet 208b. In this stroke, the work of the inflator supplements the power for driving the first swing scroll 11 of the blower, and energy is regenerated as the entire fuel cell system.

19 shows a modification of the tenth embodiment. FIG. 19 shows an example in which a scroll fluid machine having the structure as shown in FIG. 15 is applied to a fuel cell system using four pairs of operating chambers as an expander among eight pairs of operating chambers and another four pairs of operating chambers as blowers. have.

A blower suction port 307 is provided at the outer peripheral portion of the fifth fixed scroll 5. Air enters the fifth operating chamber 25, the sixth operating chamber 26, the seventh operating chamber 27, and the eighth operating chamber 28 from the blower inlet 307 and moves toward the inner circumference. Is compressed. The compressed air is discharged to the outside from the blower discharge port 308 provided in the second discharge cover 113b through the fifth fixed scroll through hole 5c. An inflator inlet 207b is provided in the center of the first discharge cover 113a provided in the second fixed scroll 2. The inlet of the fuel cell 122 is connected to the blower discharge port 308, and the outlet is connected to the expander inlet 207b. The exhaust air exiting the fuel cell 122 still maintains a high pressure to some extent, so that the fourth operating chamber 24, the third operating chamber 23, and the second operating chamber (the second fixed scroll through hole 2c) are maintained. 22) It enters the center of the 1st operation chamber 21, and expands, moving toward an outer periphery. At this time, the air gives the turning force to the first turning scroll 11 and the second turning scroll 12. An inflator outlet 208b is provided at the outer periphery of the second fixed scroll 2. The expanded air is discharged from the inflator outlet 208b. In this stroke, the work of the inflator supplements the power for driving the third swing scroll 13 and the fourth swing scroll 14 of the blower, and energy is regenerated as a system of the entire fuel cell.

20 shows a modification of the ninth or tenth embodiment. The heat insulating plate 3g is sandwiched between the third fixed scroll first hard plate 3e and the third fixed scroll second hard plate 3f. The expander increases the power generated by supplying fluid at a high temperature. On the other hand, the compressor consumes low temperature fluid, so that the power consumption is low. Thus, the hot fluid is introduced into the operating chambers 23 and 24 through the expander inlet 207b and the second fixed scroll through hole 2c so as to be heated by the heater 120. On the other hand, the low-temperature fluid sufficiently cooled by the cooler 121 is introduced into the operation chambers 21 and 22 through the compressor suction port 207a.

In this case, the first fixed scroll 1, the first turning scroll 11, the third fixed scroll wrap 3a and the third fixed scroll first hard plate 3e of the compressor become relatively low temperature. In addition, the second fixed scroll 2, the second swing scroll 12, the third fixed scroll wrap 3b and the third fixed scroll second hard plate 3f of the inflator become relatively high temperature. However, if the amount of heat transfer due to heat conduction is large between the third fixed scroll wrap 3a of the compressor and the third fixed scroll wrap 3b of the expander, the third fixed scroll wrap 3a cannot maintain a low temperature and consume the compressor. The power increases, and the third fixed scroll wrap 3b cannot maintain a high temperature and the power generated by the expander decreases. In other words, the amount of power generated as a power difference between the expander and the compressor decreases.

Thus, in this embodiment, the heat insulating plate 3g is sandwiched between the third fixed scroll first hard plate 3e of the compressor and the third fixed scroll second hard plate 3f of the expander, so that the amount of heat transfer due to heat conduction therebetween is reduced. Doing. This does not reduce the amount of power generated by the power difference between the inflator and the compressor.

[11] Eleventh Embodiment

21 shows an eleventh embodiment. The same components as those in the second embodiment use the same symbols and names, and descriptions thereof are omitted. The discharge cover 113 hangs on the outer surface of the hard plate of the second fixed scroll 2. A balance bearing (guide mechanism) 51 rests inside the discharge cover 113. The rotating cylinder 80 is integrally attached to the balance bearing inner ring 52. The fan shaft 81 is integrally attached to the rotating cylinder 80. A fan 82 depends on the fan shaft 81. The outer circumferential surface of one end of the pivot shaft 104b pivots while inscribed on the inner surface of the rotary cylinder 80. Therefore, the rotating cylinder 80 rotates with the balance bearing inner ring 52, the fan shaft 81 also rotates, and the fan 82 rotates. The rotary cylinder 80 is sealed inside and outside by a seal ring 83 attached to the discharge cover 113. Therefore, in the case of a compressor, the fluid is sucked in the inlet 107, compressed into the first operating chamber 21, the second operating chamber 22, and introduced into the casing 100 through the first fixed scroll through hole 1c. Then, it is discharged to the outside from the discharge port 108. When the fan 82 rotates, outside air is taken in by the intake port 84 and blown to the outer surface of the second fixed scroll 2 to cool the second fixed scroll 2. After that, it is discharged to the exhaust port 85. According to this configuration, the fan 82 can be rotated by the turning motion of the turning shaft 104 without a special driving device such as an electric motor, and the second fixed scroll 2 can be cooled. Therefore, the number of parts of the scroll fluid machine can be reduced, thereby reducing the cost.

22 to 24 show a method of attaching (installing) the swing scroll to the swing drive section 104a or the second swing drive section 104d in all embodiments. The cross sections of the swing driver 104a and the second swing driver 104d are non-circular. The openings in the centers of the turning scroll 10 and the first to fourth turning scrolls 11, 12, 13, 14 fitted with the turning drive part 104a and the second turning drive part 104d have the same non-circular shape. have. In the example of FIG. 22, the cross section of the swing drive part and the hole of the swing scroll have the shape of a triangular curved surface, the shape of a circle having a planar cut in part in the example of FIG. 23, and the shape of a rectangle in the example of FIG. Since the fit is made into such a shape, the turning drive part 104a, the second turning drive part 104d, and the turning scroll do not rotate relatively. Therefore, when the rotation of the pivot shaft 104 is prevented, the rotation of the pivot scrolls 10, 11, 12, 13, 14 is also prevented.

In addition, the fitting of the swing drive part 104a or the second swing drive part 104d with the hole of the swing scroll is a loose fit. Therefore, the turning scrolls 10, 11, 12, 13, 14 can move on the turning drive part 104a and the second turning drive part 104d in the axial direction. Therefore, even if the turning shaft 104 changes dimension by thermal expansion, the turning scrolls 10, 11, 12, 13, 14 are not loaded in the axial direction. The swinging scrolls 10, 11, 12, 13, 14 are positioned by sandwiching between the fixed scrolls with a slight gap between each lap tip and the slab face. Therefore, excessive force is not generated on the tip of the wrap, and loss, abrasion, and shaving due to friction of the wrap tip can be prevented.

[12] Twelfth Embodiment

25 and 26 show a twelfth embodiment. In FIG. 25, a self-lubricating cylindrical member 116 is attached to the anti-rotation bearing inner ring 112. The anti-rotation pin 110 pivots while inscribed to the cylindrical member 116. In this case, if the outer diameter of the anti-rotation pin 110 is d1, the inner diameter of the cylindrical member 116 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the inner gap of the bearing is δ. , d1, D1, ε, and δ are set to have a relationship with Equation 1.

In FIG. 26, a self-lubricating cylindrical member 53 is attached to the balance bearing inner ring 52. The pivot shaft one end 104b or the pivot shaft other end 104c pivots while inscribed in the cylindrical member 53. In this case, the outer diameter of one end of the pivot shaft 104b or the other end of the pivot shaft 104c is d2, the inner diameter of the cylindrical member 53 is D2, and the turning radius of the pivot shaft 104 when the fluid machine is operated. If ε and the bearing internal clearance are δ, d2, D2, ε, and δ are set to have the relation of Equation 2.

As for the material of the cylindrical member 116 or 53, the material generally called a dry bearing or a non-lubricated bearing is suitable. Examples of the material include a resin mainly composed of a material having excellent self-lubricating properties such as ethylene tetrafluoride and excellent sliding properties, a metal coated with this resin, a resin impregnated with oil or a sintered metal, and molybdenum dihydride. Or a resin or metal impregnated with or coated thereon.

By setting it as such a structure, the lubrication of the contact surface of the cylindrical member 116 and the anti-rotation pin 110 improves, and the wear of the anti-rotation pin 110 can be reduced. Or the lubrication of the contact surface of the cylindrical member 53 and the other end 104c of the pivot shaft improves, and the abrasion of the other end 104c of the pivot shaft can be reduced.

[13] Example 13

27 shows a thirteenth embodiment. Seal rings 48 are mounted on both sides of the pivoting scroll central portion 10d. The seal ring 48 has a diameter which does not push out the first fixed scroll through hole 1c and the second fixed scroll through hole 2c even when the swinging scroll 10 is eccentrically moved. The seal ring 48 slides with the tooth bottom of the 1st fixed scroll 1 and the 2nd fixed scroll 2, and seals the operation chamber 21 and 22 and the exterior. The discharge port 108 is provided in the hard plate portion of the second fixed scroll 2 and communicates with the central operating chamber. In addition, the swing plate communication hole 10c is provided at the center portion of the swing plate 10 of the swing scroll 10. Therefore, the fluid sucked into the suction port 107 and compressed into the operation chambers 21 and 22 does not go out from the first fixed scroll through hole 1c and the second fixed scroll through hole 2c to the outside, and the discharge port is discharged. In 108, it is discharged to the outside. Although the cover 117 rests on the fixed scroll 2, no fluid flows into the cover. According to the thirteenth embodiment, the anti-rotation bearing (guide mechanism) 111 is not in the fluid path. Therefore, the anti-rotation bearing (guide mechanism) 111 does not become high temperature and does not corrode even when handling corrosive fluids.

1st fixed scroll
2 2nd fixed scroll
3 3rd fixed scroll
3g insulation board
4th Fixed Scroll
5 5th fixed scroll
6 Sixth Fixed Scroll
10 turning scrolls
11 First Turn Scroll
12 Second Turn Scroll
13 Third Turn Scroll
14 4th Turn Scroll
36 vents
50 bearing blocks
51 Balance Bearing (Guide)
51a First balance bearing (guide mechanism)
51b 2nd Balance Bearing (Guide)
52 Balanced bearing inner ring
52a inner balance bearing inner ring
52b Second balance bearing inner ring
53 Cylindrical Member
60 anti-rotation plate
61 anti-rotation pin
62 anti-rotation bearing (anti-rotation guide)
63 anti-rotation bearing inner ring
64 Rotating Prevention Sliding Member (Rotating Prevention Guide)
71 outlet
84 Intake vent
85 exhaust vent
100 casing
101 rotary bearing
102 axis of rotation
103 slewing bearing
104 pivot
104a swing drive
104b pivot end
104c pivot other end
104d second turning drive
107 Suction Inlet
108 outlet
109 anti-rotation plate
110 anti-rotation pin
111 Anti-Rotary Bearings (Guide)
112 anti-rotation bearing inner ring
113 discharge cover
114 discharge chamber
115 Anti-rotation sliding member (guide mechanism)
116 Cylindrical Member
117 cover
207a compressor inlet
207b inflator inlet
208a compressor outlet
208b inflator outlet
307 blower inlet
308 blower outlet

Claims (39)

A stator fixed to the casing, the rotating shaft rotatably supported by the casing, a rotor fixed to the rotating shaft, a rotating shaft eccentrically supported rotatably on the rotating shaft, and rotation preventing means for preventing rotation of the rotating shaft; In a fluid machine having an operating part fitted to a swing drive part of a pivot shaft and having a combination of a swing scroll having a spiral wrap on both sides and a fixed scroll fixed to one end of the casing,
Pivot axis penetrates the operating part,
With the guide mechanism, which is a rolling bearing, on the outermost fixed scroll,
One end of the pivot is guided by the guide mechanism,
The guide mechanism is a balance bearing,
A scroll fluid machine which pivots while inscribed in the inner ring of a balance bearing provided at the center of a fixed scroll whose outer peripheral surface of the pivot shaft is located at the outermost position. A stator fixed to the casing, the rotating shaft rotatably supported by the casing, a rotor fixed to the rotating shaft, a rotating shaft eccentrically supported rotatably on the rotating shaft, and rotation preventing means for preventing rotation of the rotating shaft; In a fluid machine having an operating part fitted to a swing drive part of a pivot shaft and having a combination of a swing scroll having a spiral wrap on both sides and a fixed scroll fixed to one end of the casing,
Pivot axis penetrates the operating part,
With the guide mechanism, which is a rolling bearing, on the outermost fixed scroll,
One end of the pivot is guided by the guide mechanism,
The guide mechanism is an anti-rotation guide fixed to the outermost fixed scroll,
Anti-rotation board attached to one end of the pivot,
Anti-rotation pins attached to at least two places of the anti-rotation plate,
The rotation prevention means is comprised by the rotation prevention guide which is a rolling bearing,
A scroll fluid machine that rotates while the anti-rotation pins inscribe in the inner ring of the anti-rotation guide. delete delete delete delete delete delete delete delete delete The method of claim 1, further comprising:
One end of the pivot,
A scroll fluid machine characterized in that the portion in contact with the inner ring of the balance bearing, which is a rolling bearing, is curved in the axial direction.

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