JP5433831B2 - Scroll fluid machinery - Google Patents

Description

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

  The scroll fluid machine has a fixed scroll in which a spiral wrap is erected on an end plate, and an operation unit configured by combining similar orbiting scrolls. When the orbiting scroll is fixed to the shaft of the driving device and is rotated without rotating, the working fluid flowing from the suction pipe is compressed and discharged from the discharge pipe, thereby functioning as a compressor or a blower. When the high-pressure working fluid flowing from the inlet of the fixed scroll is expanded and discharged from the outlet, it functions as an expander that extracts power from the shaft of the drive device.

  An eccentric turning drive device having a turning shaft has been proposed as a drive device used in a scroll fluid machine. For example, a scroll fluid machine disclosed in Japanese Patent No. 3761503 has an eccentric turning drive device and a fluid machine body driven by the eccentric turning drive device. The turning shaft of the eccentric turning drive device is attached to penetrate the turning scroll of the fluid machine main body. On both sides of the orbiting scroll, there are first and second eccentric orbiting support means for supporting the orbiting shaft so as to be eccentrically rotatable with respect to the fixed scroll of the fluid machine body.

  In this scroll fluid machine, orbiting bearings that support the orbiting shaft are provided on both sides of the orbiting scroll. A rotary bearing is provided on the outer side of both rotary bearings via a rotating body whose axis coincides with the rotary shaft of the eccentric rotary drive device. For this reason, the rotary bearing is driven by the slewing shaft during operation, but since a mechanism for synchronously rotating both slewing bearings is not provided, the rotational resistance of the rotary bearing and the slewing bearing is applied in the movement direction of the slewing shaft. As a result, the smooth drive of the swivel shaft is hindered, and there is a risk that the laps will come into contact with each other to generate noise, and the lap may be worn or seized. It is an object of the present invention to provide a structure that prevents the wraps from contacting each other and prevents noise, wrap wear and seizure, so that the swivel shaft can be smoothly driven and prevented from swinging.

  The present invention has been made to solve the above problems. The present invention provides a highly reliable scroll fluid machine that has a structure with less resistance in the direction of motion and that does not generate vibration noise due to contact between the laps, and that the laps are not worn or seized. Main features. For this reason, even if the rotational speed increases and the centrifugal force of the orbiting scroll increases, or the differential pressure between the discharge pressure and the suction pressure increases and the radial load acting on the orbiting shaft increases, Means are provided to prevent displacement in the direction.

  In the present invention, the swivel shaft that is eccentrically supported by the rotation shaft and rotatably supported, the rotation prevention means for preventing the rotation of the swivel shaft, and the swivel drive portion of the swivel shaft are fitted into a spiral wrap on both sides. In a fluid machine having an actuating portion configured by combining a turning scroll having a pair and a pair of fixed scrolls fixed to one end of the casing, the orbiting shaft passes through the actuating portion and guides the fixed scroll located at the outermost portion. And one end of the swivel shaft is guided by the guide mechanism and swivels to generate a load that cancels a radial load acting on the swivel shaft. This prevents the turning scroll from being displaced or tilted beyond the set turning radius. The guide mechanism is a rotation prevention guide or a balance bearing attached to the outermost fixed scroll. The anti-rotation guide guides anti-rotation pins attached at two or more positions on the anti-rotation plate attached to the tip of the turning shaft. The balance bearing guides the tip of the pivot shaft.

  According to the scroll fluid machine of the present invention, one end of the orbiting shaft is guided by the guide mechanism to perform the orbiting motion, whereby a radial load acts on the orbiting shaft. In the guide mechanism, a load that cancels the load acting in the radial direction of the turning shaft is generated. Thereby, 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 high speed and the centrifugal force of the orbiting scroll is large, the orbiting scroll wrap and the fixed scroll lap contact each other to generate vibration noise, wear, or seizure. Do not do. Therefore, a highly reliable scroll fluid machine can be provided.

FIG. 1 is an axial sectional view showing a first embodiment.
2 is a cross-sectional view taken along the line AA in FIG.
FIG. 3 is a partial cross-sectional view showing a modification of the first embodiment.
FIG. 4 is an axial sectional view showing another modification of the first embodiment.
FIG. 5 is an axial sectional view showing a first reference example .
6 is a cross-sectional view taken along the line AA in FIG.
FIG. 7 is an axial sectional view showing a modification of the first reference example .
FIG. 8 is an axial sectional view showing a second reference example .
FIG. 9 is an axial sectional view showing a third reference example .
FIG. 10 is an axial sectional view showing a fourth reference example .
FIG. 11 is an axial sectional view showing a fifth reference example .
FIG. 12 is an axial sectional view showing a sixth reference example .
FIG. 13 is an axial sectional view showing a modification of the sixth reference example .
FIG. 14 is an explanatory diagram of a scroll wrap combination state in FIG.
FIG. 15 is an axial sectional view showing a seventh reference example .
FIG. 16 is an axial sectional view showing a modification of the seventh reference example .
FIG. 17 is an axial sectional view showing an eighth reference example .
FIG. 18 is an axial sectional view showing a ninth reference example .
FIG. 19 is an axial sectional view showing a modification of the ninth reference example .
FIG. 20 is an axial sectional view showing a modification of the eighth reference example or the ninth reference example .
FIG. 21 is an axial sectional view showing a tenth reference example .
FIG. 22 is a partial cross-sectional view showing a first example of the coupling portion between the orbiting scroll and the orbiting drive shaft.
FIG. 23 is a partial cross-sectional view showing a second example of the coupling portion between the orbiting scroll and the orbiting drive shaft.
FIG. 24 is a partial cross-sectional view showing a third example of the coupling portion between the orbiting scroll and the orbiting drive shaft.
FIG. 25 is a partial cross-sectional view showing a portion of an anti-rotation bearing of an eleventh reference example .
FIG. 26 is a partial cross-sectional view showing a balance bearing portion of an eleventh reference example .
FIG. 27 is an axial sectional view showing a twelfth reference example .

Explanation of symbols

1 First fixed scroll
2 Second fixed scroll
3 Third fixed scroll
3g insulation board
4 Fourth fixed scroll
5 Fifth fixed scroll
6 6th fixed scroll
10 Orbiting scroll
11 First orbiting scroll
12 Second orbiting scroll
13 Third orbiting scroll
14 4th scroll
36 Vent
50 Bearing block
51 Balance bearing (guide mechanism)
51a 1st balance bearing (guide mechanism)
51b Second balance bearing (guide mechanism)
52 Balance bearing inner ring
52a 1st balance bearing inner ring
52b Inner ring of second balance bearing
53 Cylindrical member
60 Anti-rotation plate
61 Anti-rotation pin
62 Anti-rotation bearing (rotation prevention guide)
63 Anti-rotation bearing inner ring
64 Anti-rotation sliding member (Anti-rotation guide)
71 Discharge port
84 Air intake
85 Exhaust port
100 casing
101 slewing bearing
102 Rotation axis
103 Slewing bearing
104 swivel axis
104a Swiveling drive
104b One end of pivot axis
104c Rotating shaft other end
104d Second turning drive
107 Suction port
108 Discharge port
109 Anti-rotation plate
110 Anti-rotation pin
111 Anti-rotation bearing (guide mechanism)
112 Anti-rotation bearing inner ring
113 Discharge cover
114 Discharge chamber
115 Anti-spinning sliding member (guide mechanism)
116 Cylindrical member
117 Cover
207a Compressor inlet
207b Expander inlet
208a Compressor outlet
208b Expander outlet
307 Blower inlet
308 Blower outlet

[1] First Embodiment FIG. 1 shows a first embodiment. FIG. 2 is a cross-sectional view taken along the line AA in FIG. The anti-wrap surface of the first fixed scroll 1 having a spiral wrap is fixed to the casing 100 on the end plate. The orbiting scroll 10 having a spiral wrap is installed on the end plate so as to overlap the first fixed scroll 1, and the second fixed scroll 2 having the spiral wrap is installed on the end plate so as to overlap the orbiting scroll 10. It is fixed to the scroll 1. The first fixed scroll 1, the orbiting scroll 10 and the second fixed scroll 2 constitute an operating part. The first fixed scroll wrap 1 a and the orbiting scroll wrap 10 a provided on the orbiting scroll 10 are combined to constitute a set of first working chambers 21. The orbiting scroll wrap 10b provided on the orbiting scroll 10 and the second fixed scroll wrap 2a are combined to constitute a set of second working chambers 22.

The outer ring of the rotary bearing 101 is installed in the casing 100 at two locations. A rotary shaft 102 is fitted to the inner ring of the rotary bearing 101. A motor stator 105 is fixed to the casing 100, and a motor rotor 106 is fixed to the rotating shaft 102. Further, a balancer 47 for balancing the entire centrifugal force is attached to the rotating shaft 102. The rotary shaft 102 is provided with bearing housings at both ends of the position eccentric from the rotation center, and the outer ring of the swivel bearing 103 is installed in the bearing housing. A turning shaft 104 is fitted to the inner ring of the turning bearing 103. The turning shaft 104 passes through the first fixed scroll through hole 1c. A hole is provided in the center of the orbiting scroll 10. The hole is fitted to the turning drive unit 104a without relative rotation. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. An anti-rotation plate 109 is fixed to one end 104b of the turning shaft. As shown in FIG. 2, anti-rotation pins 110 are embedded at three positions on the inner surface side of the anti-rotation plate 109. An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2 as an anti-rotation guide. The anti-rotation plate 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111 constitute an anti-rotation means. The anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112. When the outer diameter of the rotation prevention pin 110 is d1, the inner diameter of the rotation prevention bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d1, D1, The following relationship is set between ε and δ.

2ε−δ ≦ D1−d1 ≦ 2ε + δ (Formula 1)

When the value of D1-d1 is set in this way, the anti-rotation pin 110 is kept in contact with the anti-rotation bearing inner ring 112, and the rotation of the turning shaft 104 is reliably prevented. Further, the turning shaft one end 104b is not bent inward by a strong force. Therefore, no noise is generated and the mechanical loss is reduced. Even if the centrifugal force of the orbiting scroll 10 acts on the orbiting drive unit 104a, the orbiting shaft one end 104b does not bend any more when the bearing internal clearance of the rotation preventing bearing (guide mechanism) 111 becomes zero. Thereby, the contact of the scroll wrap can be prevented. Therefore, even if the scroll fluid machine has a large orbiting scroll, it can rotate at a higher speed than before.

  A discharge cover 113 is fixed to the outer surface of the second fixed scroll 2 so as to seal the discharge chamber 114. The discharge cover 113 includes a rotation prevention plate 109 and a rotation prevention bearing (guide mechanism) 111. A discharge port 108 is provided in the discharge cover 113. A suction port 107 is provided on the outer peripheral portion of the second fixed scroll 2.

  Next, the operation of the scroll fluid machine will be described. When the windings of the stator 105 are energized, the rotor 106 rotates, the rotating shaft 102 rotates, and the rotating shaft 104 is prevented from rotating and driven eccentrically as described later. A turning drive unit 104a, which is a part of the turning shaft 104, drives the turning scroll 10 to turn. A first working chamber 21 composed of the first fixed scroll wrap 1a and the orbiting scroll wrap 10a and a second working chamber 22 composed of the second fixed scroll wrap 2a and the orbiting scroll wrap 10b move from the outer peripheral side to the inner peripheral side. However, the volume is reduced and the internal fluid is compressed. At the center of the end plate of the orbiting scroll 10, a revolving end plate communication port 10c is provided. Therefore, the working chamber 21 and the working chamber 22 communicate with each other at the center. As a result, the fluid is sucked from the suction port 107, compressed through the suction chamber 130, joined to the working chamber 22 side, flows into the discharge chamber 114 through the second fixed scroll through-hole 2 c, and is discharged to the discharge port 108. Discharged from the outside.

  Since there is a relationship of Equation 1 between the outer diameter d1 of the rotation prevention pin 110 and the inner diameter D1 and the turning radius ε of the rotation prevention bearing inner ring 112, the rotation prevention pin 110 always has a certain amount of space between the rotation prevention bearing inner ring 112 and the rotation prevention bearing inner ring 112. Swing motion while maintaining contact force. Since the anti-rotation plate 109 has the anti-rotation pins 110 at two or more places on the anti-rotation plate 109, the anti-rotation plate 109 rotates but cannot rotate. Since the rotation prevention plate 109 is fixed to the turning shaft one end 104b, the turning shaft 104 is turned and prevented from rotating. Further, since the orbiting scroll 10 is fitted to the orbiting drive unit 104a without being relatively rotated, the orbiting scroll 10 is prevented from rotating and is orbited.

  Incidentally, since the orbiting scroll 10 has a mass, a centrifugal force is generated in a direction perpendicular to the axis when it orbits. The entire centrifugal force is canceled by the balancer 47. However, the centrifugal force becomes a load that attempts to displace the orbiting scroll in the radial direction about the shaft. This load is a load for bending the turning drive unit 104a. The turning drive unit 104a bends in the direction of the combined load with the turning bearing 103 as a fulcrum. As a result, the orbiting scroll 10 is also displaced while being inclined in the direction of the combined load. For this reason, the orbiting scroll wraps 10a and 10b approach the first fixed scroll wrap 1a and the second fixed scroll wrap 2a. If the laps come too close, the gap between the laps, which was originally set to be small in order to suppress leakage, becomes zero, and sliding begins. Then, sliding loss occurs in the wrap. Further, vibration noise is generated in the scroll fluid machine. Furthermore, wear of the lap progresses, and seizure occurs between the laps. That is, both the performance and reliability of the scroll fluid machine are impaired.

  However, according to the present invention, since the rotation prevention pin 110 is in contact with the rotation prevention bearing inner ring 112, the turning shaft one end 104 b cannot be displaced beyond the turning radius determined by the rotation prevention pin 110 and the rotation prevention bearing inner ring 112. Therefore, even if the turning scroll 10 rotates at a high speed and the centrifugal force increases to increase the load for bending the turning drive unit 104a, the turning drive unit 104a is prevented from being bent. Therefore, rap comrades do not touch. Therefore, the scroll fluid machine of the present invention can achieve a higher speed rotation than the conventional one even if it has a large orbiting scroll.

  FIG. 3 is a partial sectional view showing a modification of the first embodiment. As shown in FIG. 3, a rotation preventing sliding member (guide mechanism) 115 is used instead of the rotation preventing bearing (guide mechanism) 111 as the rotation preventing guide. The anti-rotation plate 109, the anti-rotation pin 110 and the anti-rotation sliding member (guide mechanism) 115 constitute an anti-rotation means. The rotation preventing sliding member (guide mechanism) 115 is made of a self-lubricating member such as resin. Since the rotation prevention pin 110 is guided to make a turning motion while being inscribed in the inner surface of the rotation prevention sliding member (guide mechanism) 115, the rotation of the turning shaft 104 and the turning scroll 10 is prevented, and the turning shaft one end 104b is rotated. It cannot be displaced beyond the turning radius determined by the prevention pin 110 and the rotation prevention sliding member (guide mechanism) 115.

  By doing so, the rotation prevention pin 110 and the rotation prevention sliding member (guide mechanism) 115 are in contact with each other, and thus the rotation of the orbiting scroll is reliably prevented. Even if the centrifugal force of the orbiting scroll 10 acts on the orbiting drive unit 104a, the orbiting shaft one end 104b does not bend after the rotation preventing pin 110 and the rotation preventing sliding member (guide mechanism) 115 are in contact with each other. Thereby, contact of laps can be prevented. Therefore, even if the scroll fluid machine according to the present invention has a large orbiting scroll, it can perform a revolving motion at a higher speed and with higher accuracy than the conventional one.

  FIG. 4 shows another modification of the first embodiment. FIG. 4 shows an example in which cooling is performed by providing a fan 31 at the rotating shaft rear end 102a when the first embodiment is a vacuum pump. The bearing board 35 is provided with a vent hole 36 therethrough. An exhaust port 34 is provided on the side surface of the casing 100 on the side closer to the first fixed scroll 1 than the stator 105. The turning shaft 104 is provided with a turning shaft ventilation passage 32 penetrating therethrough. The bottom plate 100a of the casing 100 has a hole, and the filter 30 is attached. When the fan 31 rotates together with the rotating shaft 102, air is taken in from the outside through the filter 30. The air that has entered from the filter 30 passes through the vent 36 and passes through the motor space 33 in the casing 100 and is discharged to the outside from the exhaust 34. During this time, the rotary bearing 101 and the stator 105 are cooled, and an excessive temperature rise is prevented. Further, the air that has entered from the filter 30 exits the fan 31, flows into the discharge chamber 114 through the swirl shaft air passage 32, and is discharged along with the air discharged from the first working chamber 21 and the second working chamber 22. 108 is discharged to the outside. During this time, the central portions of the orbiting bearing 101 and the orbiting scroll 10 are cooled, and an excessive temperature rise is prevented.

  FIG. 4 also shows an example in which a seal member for sealing the space on the working chamber side and the casing side is provided when the first embodiment of the present invention is a vacuum pump. The ring-shaped inner surface seal 42 is attached so as to surround the first fixed scroll through hole 1c. The seal plate 40 is attached to the pivot shaft 104 so as to contact the inner surface seal 42. The seal cover 41 is attached to the casing side facing the seal plate 40. The ring-shaped outer surface seal 43 is attached to the seal cover 41 and is in contact with the seal plate 40. With this configuration, the space on the working chamber side and the space on the casing side are sealed twice with the first fixed scroll through hole 1c interposed therebetween. Therefore, the gas exiting the working chamber is reliably prevented from leaking into the casing. Further, the discharged gas is blocked from the outside air by the discharge cover 113 and is exhausted 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 into the outside air.

[0021]
[2] First reference example Fig. 5 shows a first reference example . 6 is a cross-sectional view taken along the line AA in FIG. The same parts as in the first embodiment use the same symbols and names, and the description thereof is omitted. The discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2. The balance bearing (guide mechanism) 51 is attached inside the discharge cover 113. The outer peripheral surface of the turning shaft one end 104b turns 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 pivot radius of the pivot shaft 104 when the scroll fluid machine is operated is ε, and the bearing internal clearance is δ, d2,
D2, ε, and δ are set to have the following relationship.
[Expression 2]
2ε−δ ≦ D2−d2 ≦ 2ε + δ (Formula 2)
Thus, when the value of D1-d1 is set, the turning shaft one end 104b is kept in contact with the balance bearing inner ring 52 substantially. Further, the turning shaft one end 104b is not bent inward by a strong force. Therefore, no noise is generated and the mechanical loss is reduced. Even if the centrifugal force of the orbiting scroll 10 acts on the orbiting drive unit 104a, the orbiting shaft end 104b does not bend any more when the bearing internal clearance of the balance bearing (guide mechanism) 51 becomes zero. Thereby, the contact of the scroll wrap can be prevented. Therefore, even if the scroll fluid machine has a large orbiting scroll, it can rotate at a higher speed than before.

The rotation prevention plate 60 is fixed to the other end 104c of the turning shaft. The anti-rotation pins 61 are embedded at two or more locations on the anti-rotation plate 60. The rotation prevention bearing 62 is attached to the bottom plate 100 a of the casing 100. The rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63. If the outer diameter of the rotation prevention pin 61 is d3, the inner diameter of the rotation prevention bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d3, D3, The following relationship is set between ε and δ.

2ε−δ ≦ D3−d3 ≦ 2ε + δ (Formula 3)

When the value of D1-d1 is set in this manner, the rotation prevention pin 61 is kept in contact with the rotation prevention bearing inner ring 63. Therefore, the rotation of the orbiting scroll 10 is reliably prevented. Further, the turning shaft other end 104c is not bent inward by a strong force. Therefore, no noise is generated and the mechanical loss is reduced.

FIG. 7 shows a modification of the first reference example . As shown in FIG. 7, the turning shaft one end 104b has a barrel shape having a curved surface in the axial direction. In this way, the swivel shaft one end 104b does not come into contact with the balance bearing inner ring 52. Therefore, galling and wear are less likely to occur on the surface where the pivot shaft end 104b and the balance bearing inner ring 52 come into contact. Therefore, the reliability of the scroll fluid machine is increased. Further, the anti-rotation sliding member 64 is used as a guide for the anti-rotation pin 61 attached to the anti-rotation plate 60. The rotation preventing sliding member 64 is made of a self-lubricating member such as resin. The rotation preventing sliding member 64 may be made of a wear-resistant surface-treated metal member.

[3] Second reference example Fig. 8 shows a second reference example . The cover 70 seals the outer surface of the center portion of the second fixed scroll 2 and blocks the working chamber side and the atmosphere side. Further, the discharge port 71 is provided on the bottom side of the stator 105 on the outer periphery of the casing 100. The fluid flows in from the suction port 107, is compressed in the first working chamber 21 and the second working chamber 22, enters the casing 100 from the first fixed scroll through-hole 1 c, passes through the inside of the casing 100, and discharges 71. Discharged from the outside. According to this structure, a simple cover 70 is sufficient instead of the discharge cover 113. Therefore, in the scroll fluid machine, one machining part can be reduced and the cost can be reduced. Further, since the protrusion is eliminated, the overall length can be shortened, and the inside of the casing can be cooled by the movement of the working fluid.

[4] Third reference example Fig. 9 shows a third reference example . The fluid machine shown in FIG. 9 is a twin-type scroll fluid machine having scrolls at both ends of the turning shaft 104. The anti-wrap surface of the first fixed scroll 1 is fixed to the right side of the casing 100. A first orbiting scroll 11 is installed on the first fixed scroll 1. A second fixed scroll 2 is installed over the first orbiting scroll 11 and is fixed to the first fixed scroll 1. The first fixed scroll 1, the first orbiting scroll 11 and the second fixed scroll 2 constitute an orbiting shaft one end side operating portion. The first fixed scroll wrap 1a and the first orbiting scroll wrap 11a are combined to constitute a set of first working chambers 21. The first orbiting scroll wrap 11b and the second fixed scroll wrap 2a are combined to constitute a set of second working chambers 22. A first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11. Thereby, the first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c. As a result, the fluid is sucked from the first suction port 107a, is compressed through the first suction chamber 131, merges into the working chamber 22 side, passes through the second fixed scroll through-hole 2c, and enters the first discharge cover 113a. Into the first discharge chamber 114a and discharged from the first discharge port 108a to the outside.

  The anti-wrap surface of the third fixed scroll 3 is fixed to the left side of the casing 100. A second orbiting scroll 12 is installed on the third fixed scroll 3. A fourth fixed scroll 4 is installed on the second orbiting scroll 12 and is fixed to the third fixed scroll 3. The third fixed scroll 3, the second orbiting scroll 12 and the fourth fixed scroll 4 constitute an orbiting shaft other end side operation portion. The third fixed scroll wrap 3a and the second orbiting scroll wrap 12a are combined to constitute a set of third working chambers 23. The second orbiting scroll wrap 12b and the fourth fixed scroll wrap 4a are combined to constitute a set of fourth working chambers 24. The rotating shaft 102 rotates, and the turning shaft 104 is prevented from rotating and driven eccentrically. A second turning drive unit 104 d that is a part of the turning shaft 104 drives the turning scroll 12 to turn. The working fluid moves from the outer peripheral side to the inner peripheral side of the third working chamber 23 and the fourth working chamber 24, the volume is reduced, and the working fluid is compressed. A second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12. Thereby, the third working chamber 23 merges with the fourth working chamber 24 through the second swivel end plate communication port 12c. As a result, the working fluid sucked from the second suction port 107b is compressed via the second suction chamber 132, passes through the fourth fixed scroll through-hole 4c, and the second discharge chamber 114b in the second discharge cover 113b. And is discharged from the second discharge port 108b to the outside.

  The outer ring of the rotary bearing 101 is installed in the casing 100 at two locations. A rotary shaft 102 is fitted to the inner ring of the rotary bearing 101. A balancer 47 for balancing the entire centrifugal force is attached to the rotary shaft 102 at two locations. A motor stator 105 is fixed to the casing 100, and a motor rotor 106 is fixed to the rotating shaft 102. Further, a balancer 47 for balancing the entire centrifugal force is attached to the rotating shaft 102. The rotary shaft 102 is provided with bearing housings at both ends of the position eccentric from the rotation center, and the outer ring of the swivel bearing 103 is installed in the bearing housing. A turning shaft 104 is fitted to the inner ring of the turning bearing 103. The turning shaft 104 passes through the first fixed scroll through hole 1c. A hole is provided in the center of the first orbiting scroll 11. The hole is fitted to the turning drive unit 104a so as not to rotate relatively. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. The rotation prevention plate 109 is fixed to the turning shaft one end 104b. As shown in FIG. 2, the rotation prevention pins 110 are embedded at three locations on the inner surface side of the rotation prevention plate 109. An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2. The anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112. When the outer diameter of the rotation prevention pin 110 is d1, the inner diameter of the rotation prevention bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d1, D1, ε and δ are set so as to have the relationship of Equation 1.

  The turning shaft 104 passes through the third fixed scroll through hole 3c. A hole is provided in the center of the second orbiting scroll 12. The hole is fitted to the second turning drive unit 104d in a state where it does not rotate relative to the second turning drive unit 104d. The other end 104c of the turning shaft passes through the fourth fixed scroll through hole 4c and extends to the outside. The bearing block 50 is attached to the outer surface of the end plate of the fourth fixed scroll 4. The balance bearing (guide mechanism) 51 is attached inside the bearing block 50. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. If the outer diameter of the other end 104c of the swing shaft is d2, the inner diameter of the balance bearing inner ring 52 is D2, the swing radius of the swing shaft 104 when the fluid machine is operated is ε, and the internal clearance of the bearing is δ, d2, D2, ε and δ are set so as to have the relationship of Equation 2.

In this reference example , as described above, one set of scroll portions is provided on one side of the casing 100, and another set of scroll portions is provided on the opposite side of the casing 100. Therefore, in this embodiment, it is possible to produce a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100. An anti-rotation mechanism is provided at the turning shaft end 104 b on the right side of the turning shaft 104. Further, there is a relationship of Formula 1 between the outer diameter of the rotation prevention pin 110 and the inner diameter of the rotation prevention bearing inner ring 112. Therefore, the rotation of the turning shaft 104 is reliably prevented. Further, bending of the turning shaft one end 104b due to centrifugal force is prevented. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. Further, there is a relationship of Formula 2 between the other end of the turning shaft 104 c and the balance bearing inner ring 52. Therefore, bending of the other end 104c of the turning shaft due to centrifugal force is prevented.

[5] Fourth reference example Fig. 10 shows a fourth reference example . The structure of the drive unit is the same as that of the third reference example . The same parts as in the third reference example use the same symbols and names, and the description thereof is omitted. The difference between this reference example and the third reference example will be described. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. A first discharge cover 113 a is attached to the outer surface of the end plate of the second fixed scroll 2. A first balance bearing (guide mechanism) 51a is attached to the inside of the first discharge cover 113a. The outer peripheral surface of the turning shaft one end 104b turns while inscribed in the first balance bearing inner ring 52a. If the outer diameter of the pivot shaft one end 104b is d2, the inner diameter of the first balance bearing inner ring 52a is D2, the pivot radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, then d2,
D2, ε, and δ are set so as to satisfy the relationship of Equation 2.

  A second discharge cover 113 b is attached to the outer surface of the end plate of the fourth fixed scroll 4. A second balance bearing (guide mechanism) 51b is attached inside the second discharge cover 113b. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b. If the outer diameter of the other end 104c of the swing shaft is d2, the inner diameter of the second balance bearing inner ring 52b is D2, the swing radius of the swing shaft 104 when the fluid machine is operated is ε, and the internal clearance of the bearing is δ, d2 D2, ε, and δ are set so as to satisfy the relationship of Equation 2.

  An anti-rotation plate 60 is attached between the right side of the slewing bearing 103 and the end plate of the first fixed scroll 1 so as not to rotate relatively. Anti-rotation pins 61 are embedded at three locations on the outer periphery of the anti-rotation plate. An anti-rotation bearing 62 is installed on the end plate of the first fixed scroll 1. The rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63. If the outer diameter of the rotation prevention pin 61 is d3, the inner diameter of the rotation prevention bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d3, D3, ε and δ are set so as to have the relationship of Equation 3.

In this reference example , as described above, one set of scroll portions is provided on one side of the casing 100, and one set of scroll portions is also provided on the other side of the casing 100. Therefore, this reference example , like the third reference example of the present invention, can produce a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100. The outer peripheral surface of the turning shaft one end 104b turns while inscribed in the first balance bearing inner ring 52a. There is a relationship of Formula 2 between the turning shaft one end 104b and the first balance bearing inner ring 52a. Therefore, bending of the turning shaft one end 104b due to centrifugal force is prevented. Further, the outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b. There is a relationship of Formula 2 also between the other end 104c of the turning shaft and the second balance bearing inner ring 52b. Therefore, the bending of the other end 104c of the turning shaft due to the centrifugal force is prevented.

[6] Fifth reference example Fig. 11 shows a fifth reference example . The outer surface of the center portion of the second fixed scroll 2 is covered with a first cover 70a to block the working chamber side and the atmosphere side. Further, the outer surface of the central portion of the fourth fixed scroll 4 is covered with a second cover 70b to block the working chamber side and the atmosphere side. Further, the discharge port 71 is provided in a part of the side surface of the casing 100. The fluid that has exited the first working chamber 21 and the second working chamber 22 enters the casing 100 through the first fixed scroll through hole 1c. The fluid that has exited the third working chamber 23 and the fourth working chamber 24 enters the casing 100 through the third through-hole 3c. The fluid that has entered the casing 100 passes through the inside of the casing 100 and is discharged from the discharge port 71 to the outside. In this structure, simple first cover 70a and second cover 70b are sufficient as shown in FIG. 11, so that it is not necessary to use first discharge cover 113a and second discharge cover 113b as shown in FIG. Therefore, with this structure, two processed parts can be reduced, the cost can be reduced, and the total length can be shortened because there are no protrusions. Further, the inside of the casing can be cooled with the compressed working fluid.

[7] Sixth reference example Fig. 12 shows a sixth reference example . FIG. 12 shows a fluid machine having two sets of scroll units in the turning drive unit 104a. The same components as those in the first embodiment are denoted by the same symbols and names, and the description thereof is omitted. The anti-wrap surface of the first fixed scroll 1 is fixed to the casing 100. A first orbiting scroll 11 is placed over the first fixed scroll 1. The third fixed scroll 3 is installed on the first orbiting scroll 11 and is fixed to the first fixed scroll 1. A second orbiting scroll 12 is placed over the third fixed scroll 3. The second fixed scroll 2 is installed over the second orbiting 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 orbiting scroll 11, the third fixed scroll 3, the second orbiting scroll 12, and the second fixed scroll 2 constitute an operating unit. One set of first working chambers 21 is constituted by a combination of a first fixed scroll wrap 1a and a first orbiting scroll wrap 11a. One set of the second working chamber 22 is configured by a combination of the first orbiting scroll wrap 11b and the third fixed scroll wrap 3a. One set of the third working chamber 23 is configured by a combination of the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a. One set of fourth working chambers 24 is constituted by a combination of the second orbiting scroll wrap 12b and the second fixed scroll wrap 2a. Since the third fixed scroll suction communication port 3d is provided in the third fixed scroll 3, the first suction chamber 131 and the second suction chamber 132 are in communication. A first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11. Thereby, the first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c. A second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12. As a result, the third working chamber 23 joins the fourth working chamber 24 through the second swivel end plate communication port 12c. Therefore, the fluid is sucked into all the working chambers from the suction port 107 and discharged from the discharge port 108 to the outside.

The turning shaft 104 passes through the first fixed scroll through hole 1c. A hole is provided in the center of the first orbiting scroll 11. The hole is fitted to the turning drive unit 104a so as not to rotate relatively. The turning shaft 104 passes through the third fixed scroll through hole 3c. A hole is also provided in the center of the second orbiting scroll 12. The hole is fitted to the turning drive unit 104a so as not to rotate relatively. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. A discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2. A balance bearing (guide mechanism) 51 is attached inside the bearing discharge cover 113. The outer peripheral surface of the turning shaft one end 104b turns while inscribed in the balance bearing inner ring 52. If the outer diameter of the pivot shaft end 104b is d2, the inner diameter of the balance bearing inner ring 52 is D2, the pivot radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d2, D2,
ε and δ are set so that there is a relationship of Formula 2. A rotation prevention mechanism similar to that in the first reference example is incorporated in the other end 104c of the turning shaft. An anti-rotation bearing 62 is mounted on the bottom plate 100a. The anti-rotation pin 61 is kept in contact with the inner ring 63 of the anti-rotation bearing. Therefore, the rotation of the turning shaft 104 is reliably prevented.

According to this reference example , the turning shaft one end 104b and the balance bearing inner ring 52 are kept in contact with each other. As a result, even if the centrifugal force of the first turning scroll 11 and the second turning scroll 12 acts on the turning drive unit 104a, the turning shaft one end 104b does not bend any more when the bearing internal clearance of the balance bearing inner ring 52 becomes zero. Therefore, contact between laps is prevented. Moreover, even if the scroll fluid machine has a large orbiting scroll, it can rotate at a higher speed than before. In addition, a flow rate twice that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be obtained.

13 and 14 show examples in which the phases of suction and discharge are shifted in the sixth reference example . The scroll fluid machine can change the suction and discharge phases with respect to the eccentric direction of the orbiting shaft by changing the rotational direction position of the lap during assembly. As shown in FIG. 14, the first fixed scroll wrap 1a and the first orbiting scroll wrap 11a, the third fixed scroll wrap 3a and the first orbiting scroll wrap 11b, the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a, In the combination of the two fixed scroll wrap 2a and the second orbiting scroll wrap 12b, the lap phase is rotated by 90 degrees. Therefore, although the first orbiting scroll wrap 11a, the first orbiting scroll wrap 11b, the second orbiting scroll wrap 12a, and the second orbiting scroll wrap 12b are all eccentric in the same direction (the right direction in the drawing), The phases of the two working chambers are shifted by 90 degrees.

[8] Seventh reference example Fig. 15 shows a seventh reference example . The same components as those in the first embodiment are denoted by the same symbols and names, and the description thereof is omitted. The anti-wrap surface of the first fixed scroll 1 is fixed to the right side of the casing 100. A first orbiting scroll 11 is placed over the first fixed scroll 1. The third fixed scroll 3 is installed on the first orbiting scroll 11 and is fixed to the first fixed scroll 1. A second orbiting scroll 12 is placed over the third fixed scroll 3. The second fixed scroll 2 is installed over the second orbiting 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 orbiting scroll 11, the third fixed scroll 3, the second orbiting scroll 12, and the second fixed scroll 2 constitute an orbiting shaft one end side operating portion. One set of first working chambers 21 is constituted by a combination of a first fixed scroll wrap 1a and a first orbiting scroll wrap 11a. One set of the second working chamber 22 is configured by a combination of the first orbiting scroll wrap 11b and the third fixed scroll wrap 3a. A first orbiting end plate communication port 11 c is provided in the center portion of the end plate of the first orbiting scroll 11. The first working chamber 21 joins the second working chamber 22 through the first swivel end plate communication port 11c. One set of the third working chamber 23 is configured by a combination of the third fixed scroll wrap 3b and the second orbiting scroll wrap 12a. One set of fourth working chambers 24 is constituted by a combination of the second orbiting scroll wrap 12b and the second fixed scroll wrap 2a. A second orbiting end plate communication port 12 c is provided at the center of the end plate of the second orbiting scroll 12. The third working chamber 23 joins the fourth working chamber 24 through the second swivel end plate communication port 12c. Since the third fixed scroll suction communication port 3d is provided in the third fixed scroll 3, the first suction chamber 131 and the second suction chamber 132 are in communication. Further, since the third fixed scroll through-hole 3c is provided at the center of the third fixed scroll 3, the fluid sucked from the first suction port 107a is compressed in the working chambers 21, 22, 23, 24, They gather in the discharge chamber 114 in the first discharge cover 113a and are discharged from the first discharge port 108a to the outside.

  The anti-wrap surface of the fourth fixed scroll 4 is fixed to the left side of the casing 100. A third orbiting scroll 13 is installed on the fourth fixed scroll 4. The sixth fixed scroll 6 is installed on the third orbiting scroll 13 and is fixed to the fourth fixed scroll 4. A fourth orbiting scroll 14 is installed so as to overlap the sixth fixed scroll 6. The fifth fixed scroll 5 is placed on the fourth orbiting scroll 14 and is fixed to the fourth fixed scroll 4 together with the sixth fixed scroll 6. The fourth fixed scroll 4, the third orbiting scroll 13, the sixth fixed scroll 6, the fourth orbiting scroll 14 and the fifth fixed scroll 5 constitute an orbiting shaft other end side operation portion. One set of fifth working chambers 25 is constituted by a combination of the fourth fixed scroll wrap 4a and the third orbiting scroll wrap 13a. One set of sixth working chambers 26 is configured by a combination of the third orbiting scroll wrap 13b and the sixth fixed scroll wrap 6a. A third orbiting end plate communication port 13 c is provided at the center of the end plate of the third orbiting scroll 13. The fifth working chamber 25 joins the sixth working chamber 26 through the third swivel end plate communication port 13c. One set of seventh working chambers 27 is constituted by a combination of a sixth fixed scroll wrap 6b and a fourth orbiting scroll wrap 14a. One set of eighth working chambers 28 is configured by a combination of the fourth orbiting scroll wrap 14b and the fifth fixed scroll wrap 5a. A fourth orbiting end plate communication port 14 c is provided at the center of the end plate of the fourth orbiting scroll 14. As a result, the seventh working chamber 27 joins the eighth working chamber 28 through the fourth swivel end 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 are in communication. Further, since the sixth fixed scroll through-hole 6c is provided at the center of the sixth fixed scroll 6, the fluid sucked from the second suction port 107b is compressed in the working chambers 25, 26, 27, and 28, The ink is discharged to the outside from the second discharge port 108b provided in the second discharge cover 113b.

  The structure of the drive unit is the same as in the first embodiment. The turning shaft 104 passes through the first fixed scroll through hole 1c. A hole is provided in the center of the first orbiting scroll 11 and the second orbiting scroll 12. The hole is fitted to the turning drive unit 104a so as not to rotate relatively. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. An anti-rotation plate 109 is fixed to one end 104b of the turning shaft. As shown in FIG. 2, the anti-rotation pins 110 are embedded at three locations on the inner surface side of the anti-rotation plate 109. An anti-rotation bearing (guide mechanism) 111 is installed on the front side of the second fixed scroll 2 as an anti-rotation guide. The anti-rotation plate 109, the anti-rotation pin 110, and the anti-rotation bearing (guide mechanism) 111 constitute an anti-rotation means. The anti-rotation pin 110 is combined in a state in contact with the anti-rotation bearing inner ring 112. When the outer diameter of the rotation prevention pin 110 is d1, the inner diameter of the rotation prevention bearing inner ring 112 is D1, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d1, D1, ε and δ are set so as to have the relationship of Equation 1.

  The turning shaft 104 passes through the fourth fixed scroll through hole 4c. A hole is provided at the center of the third orbiting scroll 13 and the fourth orbiting scroll 14. The hole is fitted to the second turning drive unit 104d in a state where it does not rotate relative to the second turning drive unit 104d. The other end 104c of the turning shaft passes through the fifth fixed scroll through hole 5c and extends to the outside. A second discharge cover 113 b is attached to the outer surface of the end plate of the fifth fixed scroll 5. A balance bearing (guide mechanism) 51 is attached inside the second discharge cover 113b. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. If the outer diameter of the other end 104c of the rotating shaft is d2, the inner diameter of the balance bearing inner ring 52 is D2, the turning radius of the rotating shaft 104 when the fluid machine is operated is ε, and the internal clearance of the bearing is δ, d2, D2, ε and δ are set so as to have the relationship of Equation 2.

Since this reference example is configured as described above, a flow rate four times that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be obtained. The rotation prevention means provided at the turning shaft end 104b on the right side of the turning shaft 104 reliably prevents the turning shaft 104 from rotating. Further, bending of the turning shaft one end 104b due to centrifugal force is prevented. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the balance bearing inner ring 52. There is a relationship of Formula 2 between the other end 104 c of the turning shaft and the balance bearing inner ring 52. Therefore, the bending of the other end 104c of the turning shaft due to the centrifugal force is prevented.

FIG. 16 shows a modification of the seventh reference example . The structure of the drive unit is the same as in the seventh reference example . In this reference example , the same parts as those in the seventh reference example are denoted by the same symbols and names, and description thereof is omitted. The difference between this reference example and the seventh reference example will be described. One end 104b of the turning shaft passes through the second fixed scroll through hole 2c and extends outward. A first discharge cover 113 a is attached to the outer surface of the end plate of the second fixed scroll 2. A first balance bearing (guide mechanism) 51a is attached to the inside of the first discharge cover 113a. The outer peripheral surface of the turning shaft one end 104b makes a turning motion while being inscribed in the balance bearing inner ring 52a. If the outer diameter of the pivot shaft one end 104b is d2, the inner diameter of the balance bearing inner ring 52a is D2, the pivot radius of the pivot shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d2,
D2, ε, and δ are set so as to satisfy the relationship of Equation 2. Therefore, bending of the turning shaft one end 104b due to centrifugal force is prevented. The other end 104c of the turning shaft passes through the fifth fixed scroll through hole 5c and extends to the outside. A second discharge cover 113 b is attached to the outer surface of the end plate of the second fixed scroll 2. A second balance bearing (guide mechanism) 51b is attached inside the second discharge cover 113b. The outer peripheral surface of the other end 104c of the turning shaft makes a turning motion while being inscribed in the second balance bearing inner ring 52b. There is a relationship of Formula 2 also between the other end 104c of the turning shaft and the second balance bearing inner ring 52b. Therefore, the bending by the centrifugal force of the other end 104c of a turning shaft is prevented.

  An anti-rotation plate 60 is attached between the right side of the slewing bearing 103 and the end plate of the first fixed scroll 1 so as not to rotate relatively. Anti-rotation pins 61 are embedded at three locations on the outer periphery of the anti-rotation plate 60. An anti-rotation bearing 62 is installed on the end plate of the first fixed scroll 1. The anti-rotation plate 60, the anti-rotation pin 61 and the anti-rotation bearing 62 constitute an anti-rotation means. The rotation prevention pin 61 turns while inscribed in the rotation prevention bearing inner ring 63. If the outer diameter of the rotation prevention pin 61 is d3, the inner diameter of the rotation prevention bearing inner ring 63 is D3, the turning radius of the turning shaft 104 when the fluid machine is operated is ε, and the bearing internal clearance is δ, d3, D3, ε and δ are set so as to have the relationship of Equation 3.

Since this reference example is configured as described above, a flow rate four times that of a fluid machine in which one set of scroll portions is provided on one side of the casing 100 can be produced as in the seventh reference example of the present invention.

[9] Eighth reference example Fig. 17 shows an eighth reference example . Parts identical to those in the sixth reference example use the same symbols and names, and a description thereof is omitted. The third fixed scroll 3 is divided into two. The third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f are integrated in close contact with each other. A space is provided in the center of the third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f. In this space, a seal plate 44 fixed to the turning drive unit 104a is slidably sandwiched. The first seal 45 attached to the third fixed scroll first end plate 3e and the second seal 46 attached to the third fixed scroll second end plate 3f seal both surfaces of the seal plate 44. The third fixed scroll through-hole 3c is blocked in the middle by this seal.

  The first working chamber 21 and the second working chamber 22 formed by a combination of the first fixed scroll wrap 1a, the first orbiting scroll wraps 11a and 11b, and the third fixed scroll wrap 3a constitute a compressor. The third working chamber 23 and the fourth working chamber 24, which are a combination of the third fixed scroll wrap 3b, the second orbiting scroll wrap 12a, 12b, and the second fixed scroll wrap 2a, constitute an expander.

  The discharge cover 113 provided on the second fixed scroll 2 is provided with an expander inlet 207b, into which the working fluid flows. The working fluid enters the center of the fourth working chamber 24 from the second fixed scroll through-hole 2c, enters the third working chamber 23 from the second swivel end plate communication port 12c, and expands while moving toward the outer periphery. At this time, the working fluid gives a turning force to the second orbiting scroll 12. An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2. The expanded working fluid is discharged from the expander outlet 208b. A compressor suction port 207 a is provided on the outer peripheral portion of the first fixed scroll 1. The inlet of the cooler (hot water heater) 121 is connected to the expander outlet 208b, and the outlet is connected to the compressor suction port 207a. The working fluid cooled to the low temperature by the cooler 121 enters the first working chamber 21 and the second working chamber 22 from the compressor suction port 207a, and is compressed while moving toward the inner periphery. The compressed working fluid joins through the first swivel end plate communication port 11c, enters the casing 100 through the first fixed scroll through-hole 1c, and is discharged to the outside from the compressor discharge port 208a. The inlet of the heater (heat 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 and becomes high temperature, and flows into the expander from the expander inlet 207b. In this stroke, the work of the expander becomes larger than the power of the compressor, and the expander drives the compressor. The expander further drives the turning drive unit 104a to drive the turning shaft 104 eccentrically. The turning shaft 104 rotates the rotating shaft 102. The rotating shaft 102 rotates the mounted rotor 105 to generate an electromotive force in the winding of the stator 106. As a result, electric power can be extracted from the winding. That is, this fluid machine becomes a generator.

  In general, when a compressor is driven by an expander, power is transmitted as a rotational force, so that loss occurs in the bearings that support the respective drive shafts. However, in the case of the present embodiment, the expander and the compressor are mounted on the same turning drive unit 104a, so that the power is transmitted as a load and no loss occurs between the expander and the compressor. The working fluid is preferably a stable gas that does not liquefy at room temperature, such as air, nitrogen, or helium.

[10] Ninth reference example Fig. 18 shows a ninth reference example . In this reference example , in the same scroll fluid machine as in the eighth reference example , two sets of four working chambers are used as an expander, and the other two sets are used as blowers, and applied to a fuel cell system. Is shown.

  A blower suction port 307 is provided in the outer peripheral portion of the first fixed scroll 1. Air enters the first working chamber 21 and the second working chamber 22 from the blower suction port 307 and is compressed while moving toward the inner periphery. The compressed air enters the casing 100 through the first fixed scroll through-hole 1c and is discharged to the outside through the blower discharge port 308. An expander inlet 207 b is provided at the center of the second fixed scroll 2. The inlet of the fuel cell 122 is connected to the blower outlet 308, and the outlet is connected to the expander inlet 207b. The exhaust air leaving the fuel cell 122 is still kept at a certain high pressure, enters the center of the third working chamber 23 and the fourth working chamber 24 from the second fixed scroll through-hole 2c, and expands while moving toward the outer periphery. . At this time, the air gives a turning force to the second turning scroll 12. An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2. The expanded air is discharged from the expander outlet 208b. In this process, the work of the expander supplements the power for driving the first orbiting scroll 11 of the blower, and energy is regenerated as the entire fuel cell system.

FIG. 19 shows a modification of the ninth reference example . FIG. 19 shows a fuel cell system in which a scroll fluid machine having the same structure as that of FIG. 15 is used by using four of the eight working chambers as an expander and the other four working chambers as blowers. An example applied to is shown.

  A blower suction port 307 is provided in the outer peripheral portion of the fifth fixed scroll 5. Air enters the fifth working chamber 25, the sixth working chamber 26, the seventh working chamber 27, and the eighth working chamber 28 from the blower suction port 307, and is compressed while moving toward the inner periphery. The compressed air passes through the fifth fixed scroll through hole 5c and is discharged to the outside from the blower discharge port 308 provided in the second discharge cover 113b. An expander inlet 207b is provided at the center of the first discharge cover 113a installed on 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 leaving the fuel cell 122 is still kept at a high pressure to some extent, and the center of the fourth working chamber 24, the third working chamber 23, the second working chamber 22, and the first working chamber 21 from the second fixed scroll through hole 2c. Enters and expands while moving toward the outer periphery. At this time, the air gives a turning force to the first orbiting scroll 11 and the second orbiting scroll 12. An expander outlet 208 b is provided on the outer peripheral portion of the second fixed scroll 2. The expanded air is discharged from the expander outlet 208b. In this stroke, the work of the expander supplements the power for driving the third or fourth scroll 13 and 14 of the blower, and energy is regenerated as the entire fuel cell system.

FIG. 20 shows a modification of the eighth or ninth reference example . A heat insulating plate 3g is sandwiched between the third fixed scroll first end plate 3e and the third fixed scroll second end plate 3f. The power generated by the expander is increased by supplying a fluid as hot as possible. On the other hand, the power consumption of the compressor is reduced when the fluid as low as possible is sucked. Therefore, as high a fluid as possible heated by the heater 120 is caused to flow into the working chambers 23 and 24 through the expander inlet 207b and the second fixed scroll through-hole 2c. On the other hand, the low-temperature fluid sufficiently cooled by the cooler 121 is caused to flow into the working chambers 21 and 22 through the compressor suction port 207a.

  In this case, the first fixed scroll 1, the first orbiting scroll 11, the third fixed scroll wrap 3a, and the third fixed scroll first end plate 3e of the compressor have a relatively low temperature. Further, the second fixed scroll 2, the second orbiting scroll 12, the third fixed scroll wrap 3b, and the third fixed scroll second end plate 3f of the expander become relatively hot. However, if there is a large amount of heat transfer due to heat conduction 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 the power consumption of the compressor. The third fixed scroll wrap 3b cannot maintain a high temperature, and the power generated by the expander decreases. That is, the amount of power generation that can be taken out as a power difference between the expander and the compressor decreases.

Therefore, in this reference example , a heat insulating plate 3g is sandwiched between the third fixed scroll first end plate 3e of the compressor and the third fixed scroll second end plate 3f of the expander, and the amount of heat transfer due to heat conduction therebetween is reduced. Yes. In this way, the power generation amount that can be taken out as the power difference between the expander and the compressor does not decrease.

[11] Tenth reference example Fig. 21 shows a tenth reference example . The same parts as those in the first reference example use the same symbols and names, and the description thereof is omitted. A discharge cover 113 is attached to the outer surface of the end plate of the second fixed scroll 2. A balance bearing (guide mechanism) 51 is attached inside the discharge cover 113. A rotating cylinder 80 is integrally attached to the balance bearing inner ring 52. A fan shaft 81 is integrally attached to the rotating cylinder 80. A fan 82 is attached to the fan shaft 81. The outer peripheral surface of the turning shaft end 104 b makes a turning motion while being inscribed in the inner surface of the rotating 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 on the inside and outside by a seal ring 83 attached to the discharge cover 113. Therefore, in the case of the compressor, the fluid is sucked from the suction port 107, compressed in the first working chamber 21 and the second working chamber 22, flows into the casing 100 through the first fixed scroll through-hole 1c, and is discharged. It is discharged from the outlet 108 to the outside. When the fan 82 rotates, outside air is taken in from the intake port 84 and blown to the outer surface of the second fixed scroll 2, and after cooling the second fixed scroll 2, the outside air is discharged from 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 drive 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 is reduced, and the cost can be reduced.

22 to 24 show a method of attaching the orbiting scroll to the orbiting drive unit 104a or the second orbiting drive unit 104d in all the embodiments or reference examples . The cross sections of the turning drive unit 104a and the second turning drive unit 104d are non-circular. The holes formed in the centers of the orbiting scroll 10 and the first to fourth orbiting scrolls 11, 12, 13, and 14 that fit with the orbiting drive unit 104a and the second orbiting drive unit 104d have a similar non-circular shape. The cross-section of the orbiting drive unit and the orbiting scroll hole have a triangular curved surface shape in the example of FIG. 22, a circular shape partially having a plane cut in the example of FIG. 23, and a rectangular shape in the example of FIG. ing. Since the fitting has such a shape, the orbiting drive unit 104a, the second orbiting drive unit 104d and the orbiting scroll do not rotate relatively. Therefore, if the rotation of the orbiting shaft 104 is prevented, the rotation of the orbiting scrolls 10, 11, 12, 13, and 14 is also prevented.

  Moreover, the fitting of the hole of the turning drive part 104a or the 2nd turning drive part 104d and the turning scroll is a clearance fit. Therefore, the orbiting scrolls 10, 11, 12, 13, and 14 can move in the axial direction on the orbiting drive unit 104a and the second orbiting drive unit 104d. Therefore, even if the orbiting shaft 104 changes its dimensions due to thermal expansion, the orbiting scrolls 10, 11, 12, 13, and 14 do not receive a load in the axial direction. The orbiting scrolls 10, 11, 12, 13, and 14 are positioned by being pinched by the fixed scroll with a slight gap between the tip of each lap and the end plate surface. Therefore, an excessive force is not generated at the wrap tip, and loss, wear, galling, and the like due to friction at the wrap tip can be prevented.

[12] Eleventh reference example Figs. 25 and 26 show an eleventh reference example . In FIG. 25, a self-lubricating cylindrical member 116 is attached to the rotation prevention bearing inner ring 112. The rotation prevention pin 110 rotates while inscribed in the cylindrical member 116. In this case, if the outer diameter of the rotation prevention 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 bearing internal clearance is δ, d1
D1, ε, and δ are set so as to have the relationship of Equation 1.

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

  The material of the cylindrical member 116 or 53 is generally a material called a dry bearing or a non-lubricated bearing. Examples of the material include a resin whose main component is a material that is self-lubricating and excellent in slidability such as ethylene tetrafluoride, a metal coated with this resin, a resin impregnated with oil or a sintered metal, Examples thereof include a resin or metal impregnated with or coated with molybdenum sulfide.

  With this configuration, the contact surface between the cylindrical member 116 and the rotation prevention pin 110 is lubricated, and wear of the rotation prevention pin 110 can be reduced. Or the lubrication of the contact surface of the cylindrical member 53 and the other end of the turning shaft 104c is improved, and wear of the other end of the turning shaft 104c can be reduced.

[13] Twelfth reference example Fig. 27 shows a twelfth reference example . Seal rings 48 are mounted on both sides of the orbiting scroll central portion 10d. The seal ring 48 has a diameter that does not protrude from the first fixed scroll through-hole 1c and the second fixed scroll through-hole 2c even when the orbiting scroll 10 moves eccentrically. The seal ring 48 slides with the bottom surfaces of the first fixed scroll 1 and the second fixed scroll 2 to seal the working chambers 21 and 22 from the outside. The discharge port 108 is provided in the end plate portion of the second fixed scroll 2 and communicates with the central working chamber. Further, the orbiting end plate communication port 10 c is provided at the center of the end plate of the orbiting scroll 10. Therefore, the fluid sucked from the suction port 107 and compressed in the working chambers 21 and 22 is discharged from the discharge port 108 to the outside without going out from the first fixed scroll through-hole 1c and the second fixed scroll through-hole 2c. The Although the cover 117 is attached to the fixed scroll 2, no fluid flows into the cover. According to the twelfth reference example , the anti-rotation bearing (guide mechanism) 111 is not in the fluid path. Therefore, the anti-rotation bearing (guide mechanism) 111 does not reach a high temperature and is not corroded even when a corrosive fluid is handled.

  In the swivel drive mechanism, the tip of the swivel drive shaft is displaced due to centrifugal force during high-speed rotation in the conventional structure, and the orbiting scroll wrap makes strong contact with the fixed scroll wrap, causing the wrap to wear and galling or generate noise. Or Since this problem is solved by the present invention, the scroll fluid machine can be miniaturized with a high-speed rotation specification. Therefore, the present invention is highly likely to be used in vacuum pumps, fuel cell blowers, refrigerant compressors, household and packaged air conditioners, industrial air compressors, and the like that are desired to be downsized.

Claims (5)

A stator is fixed to the casing, and a rotating shaft that is rotatably supported by the casing, a rotor that is fixed to the rotating shaft, a swivel shaft that is eccentrically supported by the rotating shaft and rotatably supported, and prevents the swiveling shaft from rotating. In a fluid machine having a rotation prevention means, an orbiting scroll fitted with a swivel drive part of a turning shaft and having a spiral scroll on both surfaces and a pair of fixed scrolls fixed to one end of a casing. ,
The turning shaft passes through the operating part, the fixed scroll located at the outermost part has a guide mechanism, and one end of the turning shaft is guided by the guide mechanism to make a turning motion.
The guide mechanism is an anti-rotation guide fixed to a fixed scroll located at the outermost part, and includes an anti-rotation plate attached to one end of the turning shaft, an anti-rotation pin attached to at least two positions of the anti-rotation plate, and an anti-rotation An anti-rotation means is configured by the prevention guide, and the anti-rotation pin rotates while inscribed in the anti-rotation guide.
The anti-rotation guide is an anti-rotation bearing, and a scroll fluid machine that rotates while the anti-rotation pin is inscribed in the inner ring of the anti-rotation bearing. In claim 1,
The anti-rotation guide is a scroll fluid machine that generates a reaction force equal to the radial load generated at one end of the turning shaft and prevents the turning shaft from being displaced in the radial direction. In claim 2,
The anti-rotation guide is an anti-spinning sliding member having a circular hole, and a scroll fluid machine that rotates while the anti-rotation pin is inscribed in the anti-spinning sliding member. In any one of Claims 1 thru | or 3,
A slurling fluid machine in which a sealing mechanism for sealing the working chamber side and the casing side is provided at the center of the end plate of the fixed scroll directly connected to the casing. In claim 4,
The seal is a scroll fluid machine that seals both sides of a disk integrally attached to a pivot shaft with ring-shaped seal members.

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