JPH07286586A - Scroll type fluid device - Google Patents

Abstract

PURPOSE:To reduce friction loss by thrust load applied on a rotary scroll in a double-teeth scroll type fluid device. CONSTITUTION:In a double-teeth scroll type fluid device 1 provided with a rotary scroll 12 provided with laps 12b, 12c on both surfaces of an end plate 12a, and a pair of fixed scrolls 10, 11 disposed on both sides of the rotary scroll 12 and provided with laps 10b, 11b on one surface, a flange 20 is formed at an outer circumferential edge part of the rotary scroll 12 to be extended toward end plates 10a, 11a of the respective fixed scrolls 10, 11, and end surfaces of the flange 20 are disposed to be close to the end plates 10a, 11a of the fixed scrolls 10, 11. A shaft bearing metal 21 is disposed between the end surface of the flange 20 and the end mirror plate 10a, 11a of the fixed scroll 10, 11, and lubricating oil is supplied to this part to form a shaft bearing structure, thereby thrust load caused by leak of fluid from actuation chambers 13, 14 or self-weight of the rotary scroll 12, and applied to the rotary scroll 12 is received.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid device, and more particularly to improvement of a bearing structure of an orbiting scroll.

[0002]

2. Description of the Related Art Conventionally, as disclosed in Japanese Patent Application Laid-Open No. 3-237202 as a type of scroll type fluid device, a wrap is erected on the front surface of an end plate and the front surfaces are arranged to face each other. And a pair of fixed scrolls and a revolving scroll disposed between the fixed scrolls and having a wrap formed on both sides of the end plate to form a working chamber by meshing with the wraps of the fixed scroll. There is.

In this type of scroll type fluid device, since the working chambers are formed on both sides of the end plate of the orbiting scroll, theoretically, the loads in the thrust direction due to the fluid pressure in the working chambers cancel each other out, and the orbiting operation is performed. Thrust load does not act on the scroll.

[0004]

However, in reality, a slight amount of fluid leaks from each working chamber, and a difference in the amount of fluid leaking in each working chamber causes a difference in the respective internal pressures. Therefore, the load in the thrust direction cannot be canceled out completely, and the thrust load acts on the orbiting scroll. Further, when the fluid device is arranged in a so-called vertical type in which the crank shaft extends in the extension direction, the own weight of the orbiting scroll acts as a load in the thrust direction.

The present invention has been made in view of this point, and an object thereof is to take measures against a thrust load acting on an orbiting scroll for a double-tooth scroll type fluid device.

[0006]

In order to achieve the above object, the present invention provides a double-toothed scroll type fluid device with a thrust bearing for receiving a thrust load acting on an orbiting scroll. Specifically, the invention according to claim 1 is, as shown in FIG. 1, in which spiral wraps (10b) and (11b) are erected on the front surfaces of the end plates (10a) and (11a), and the front surfaces are mutually A pair of fixed scrolls (10), (11) fixed to the casing (2) facing each other and each fixed scroll
It is arranged between (10) and (11), and spiral wraps (12b) and (12c) are erected on both sides of the end plate (12a).
2c) is a fixed scroll (10), (11) wrap (10b), (11b)
And the orbiting scroll (12) that meshes with the working chambers (13) and (14) respectively, and the rotation of the crankshaft (8) extending from the drive mechanism (4) causes the orbiting scroll (12) to move to the fixed scroll (1).
By revolving with respect to (0) and (11), the working chambers (13) and (14)
It is premised on a scroll type fluid device in which the internal volume of is changed to compress the fluid. The orbiting scroll (12) is provided with thrust bearing means (22) for receiving a load in the thrust direction acting on the orbiting scroll (12).

According to a second aspect of the present invention, in the scroll type fluid device according to the first aspect, thrust bearing means is provided.
(22) extends from the outer peripheral edge of the orbiting scroll (12) toward the end plates (10a), (11a) of the fixed scrolls (10), (11) and between the end plates (10a), (11a). Flange (20) forming a gap in
And a bearing member (21) arranged in a gap between the flange (20) and the end plates (10a), (11a).

According to a third aspect of the present invention, in the scroll type fluid device according to the first aspect, the crankshaft (8) is
An eccentric part formed on the crankshaft (8) through the center holes (10c), (11c), (12d) formed in the fixed scrolls (10), (11) and the orbiting scroll (12), respectively. Position (8b) in the center hole (12d) of the orbiting scroll (12) and place it on the crankshaft (8).
The thrust bearing means (22) is attached to the edge of the center hole (12d) of the orbiting scroll (12) in contrast to the eccentric part (8b) which has the oil supply passage (8c) for supplying lubricating oil formed through it. By the bearing member (23) interposed between both end faces of the formed boss (12e) and the end plates (10a), (11a) of the fixed scrolls (10), (11) facing the both end faces. It has a composition made.

According to a fourth aspect of the present invention, in the scroll type fluid device according to the first aspect, the crankshaft (8) is
An eccentric part formed on the crankshaft (8) through the center holes (10c), (11c), (12d) formed in the fixed scrolls (10), (11) and the orbiting scroll (12), respectively. Position (8b) in the center hole (12d) of the orbiting scroll (12) and place it on the crankshaft (8).
On the outer peripheral surface of the eccentric part (8b), the oil supply passage (8c) for supplying lubricating oil is formed so as to penetrate the thrust bearing means (22) at the edge of the center hole (12d) of the orbiting scroll (12). It is formed on the formed boss (12e) and both end surfaces of the boss (12e) and the oil supply passage
End plates (10a), (11a) of fixed scrolls (10), (11) facing both end faces of the boss (12e) and communicating with (8c)
And a lubrication guide passage (27) for supplying lubrication oil from the lubrication passage (8c) for lubrication.

According to a fifth aspect of the present invention, in the scroll type fluid device according to the first aspect, the crankshaft (8) is
An eccentric part formed on the crankshaft (8) through the center holes (10c), (11c), (12d) formed in the fixed scrolls (10), (11) and the orbiting scroll (12), respectively. (8b) is located in the center hole (12d) of the orbiting scroll (12), the thrust bearing means (22) is attached to the center hole (12) of the orbiting scroll (12).
d) the first permanent magnets (30), (30) provided on both end faces of the boss (12e) formed on the edge, and the fixed scroll (10) facing both end faces of the boss (12e). ), (11) End plate (10a), (1
It is composed of the second permanent magnets (31), (31) provided in 1a), and the permanent magnets (30), (31) are arranged such that their magnetic pole faces face each other.

[0011]

With the above construction, the present invention provides the following actions. In the invention of claim 1, as the fluid compression operation, the orbiting scroll (12) is fixed scrolls (10), (11) by the rotation of the crankshaft (8) accompanying the drive of the drive mechanism (4). On the other hand, the orbital motion is performed while the rotation is blocked. As a result, each scroll (10), (11), (12)
The working chambers (13), (14) formed by the wraps (11b), (12b), (11b), (12c) are contracted to compress the fluid. Then, in this compression operation, the thrust load acting on the orbiting scroll (12) due to the fluid leakage from the working chambers (13) and (14) and the own weight of the orbiting scroll (12) is the thrust bearing means. Taken by (22). For this reason,
Between each scroll due to this thrust load (10), (11), (12)
The friction loss at is reduced.

[0012] In the invention according to claim 2, the orbiting scroll
The thrust load acting on (12) is due to the flange (20) and the bearing member.
It is received by the bearing means (22) consisting of (21).
Further, since the flange (20) is formed on the outer peripheral edge of the orbiting scroll (12) and a relatively large bearing area is secured, it is possible to reliably receive the load even in a situation where the thrust load is large.

According to the third aspect of the present invention, the bearing member (23) that receives the thrust load can be arranged at a position close to the oil supply passage (8c), so that the bearing member ( It is possible to reliably supply the lubricating oil to 23).

According to the fourth aspect of the invention, a part of the lubricating oil supplied from the oil supply passage (8c) passes through the oil supply guide passage (27) of the boss portion (12e) and both end surfaces of the boss portion (12e). And the end plates (10a) and (11a) of the fixed scrolls (10) and (11) are lubricated to supply high-pressure oil to the lubrication surface. Therefore, the lubricating oil can be reliably supplied to both end surfaces of the boss portion (12e) which is the thrust surface, and a sufficient oil film reaction force can be obtained.

In the fifth aspect of the invention, the orbiting scroll (12) is moved between the fixed scrolls (10) and (11) by the repulsive force between the first and second permanent magnets (30) and (31). It will be placed in a floating state in the formed space, and even if the thrust load acts on the orbiting scroll (12), the contact force between each scroll (10), (11), (12) will be sufficient. Since it becomes smaller, it is possible to reduce the friction loss between the scrolls without requiring lubricating oil.

[0016]

【Example】

(First Embodiment) Next, a first embodiment of the present invention will be described with reference to the drawings. The scroll type fluid device according to this example is used as a compressor for a refrigerator, and compresses and discharges a refrigerant gas.

As shown in FIG. 1, this scroll type fluid device (1) has a hermetic casing (2), and a scroll mechanism for sucking, compressing and discharging a refrigerant gas is provided in an upper part inside thereof. 3) but also the scroll mechanism at the bottom
A drive mechanism (4) for driving (3) is housed in each. In addition, a scroll mechanism is provided on the upper side wall of the casing (2).
At the position corresponding to (3), a suction pipe (5) for sucking the refrigerant gas is provided so as to project to the side, and the casing
Discharge pipes (6a) and (6b) for discharging the compressed refrigerant gas to the outside are respectively projected at the center position of the upper end of (2) and the lower position of the scroll mechanism (3) on the side wall. ing.

The drive mechanism (4) comprises an electric motor (7) and a crankshaft (8) connected thereto. The electric motor (7) is composed of a stator (7a) fixed to the inner wall surface of the casing (2) and a rotor (7b) inserted in the stator (7a). The lower part of the crankshaft (8) is inserted in the rotor (7b), and the fuel pump (8a) is installed at the lower end of the crankshaft (8).
Is provided, and the oil supply pump (8a) is immersed in the lubricating oil stored in the oil sump (2a) below the casing (2).
The upper part of the crankshaft (8) penetrates the scroll mechanism (3) and extends near the upper end of the casing (2).
Further, an oil supply passage (8c) for penetrating the scroll mechanism (3) with lubricating oil pumped by the oil supply pump (8a) is formed through the crankshaft (8).

The scroll mechanism (3) comprises a pair of upper and lower fixed scrolls (10), (11). Each fixed scroll (1
0) and (11) are formed integrally with the casing (2). The upper fixed scroll (10) is a disk-shaped end plate (10a)
An involute-shaped wrap (10b) is erected on the lower surface of the. Further, the central portion of the end plate (10a) of the upper fixed scroll (10) is thickly formed through the step portion, and the crankshaft
A central hole (10c) for inserting (8) is formed.

The lower fixed scroll (11) is substantially symmetrical with the upper fixed scroll (10) described above. In other words, the wrap (11b) formed in a spiral shape (involute shape) is erected on the upper surface of the disk-shaped end plate (11a). In addition, the end plate (11
The central part of a) is thickly formed through the step,
A central hole for inserting the crankshaft (8) in the center
(11c) is formed.

The fixed scrolls (10) and (11) thus formed are arranged so that the wraps (10b) and (11b) face each other.

The upper and lower fixed scrolls (10),
An orbiting scroll (12) is arranged between the (11) and (11).
This orbiting scroll (12) is a wrap formed in a spiral shape (involute shape) on the upper and lower surfaces of a disk-shaped end plate (12a).
(12b) and (12c) are erected, respectively, and are arranged so as to mesh with the wraps (10b) and (11b) of the fixed scrolls (10) and (11) facing each other.

The end plate (12a) of the orbiting scroll (12)
On the top side of, the orbiting scroll (12) top side wrap (12
The inner and outer wall surfaces of b) are the upper fixed scroll.
The outer peripheral surface and the inner peripheral surface of the wrap (10b) of (10) are in contact with each other at a plurality of locations in the spiral direction, and a working chamber (13) for compressing the refrigerant gas is formed between these contact portions. ing.
On the other hand, on the bottom side of the end plate (12a) of the orbiting scroll (12),
A working chamber (14) for compressing the refrigerant gas is similarly formed between the lower surface side wrap (12c) of the orbiting scroll (12) and the wrap (11b) of the lower fixed scroll (11).

A central hole for inserting the eccentric part (8b) of the crankshaft (8) is provided in the central part of the orbiting scroll (12).
(12d) is formed, and the edges of the center hole (12d) have substantially the same dimensions as the wraps (12b) and (12c), and the upper and lower end faces have respective fixed scrolls (10), ( A boss portion (12e) which is set to be close to the inner surface of (11) and extends vertically is formed. The eccentric portion (8b) of the crankshaft (8) has its axis (P) slightly eccentric with respect to the axis (Q) of the crankshaft (8). Therefore, when the crankshaft (8) rotates due to the drive of the drive mechanism (4), the orbiting scroll (12) revolves around the axis (Q) of the crankshaft (8) and revolves into the working chambers (13), (14). )
Is designed to contract.

Further, the discharge holes (10) for communicating the working chambers (13), (14) with the internal spaces (A), (B) of the closed casing (2).
d) and (11d) are formed on the fixed scrolls (10) and (11), respectively. Specifically, the discharge hole (10d) formed in the upper fixed scroll (10) has a working chamber (13) whose one end is on the upper side.
Of the upper fixed scroll (10) to the casing inner space (A) on the upper side, respectively, and the refrigerant gas compressed in the upper working chamber (13) flows into the upper casing inner space. It is designed to discharge to (A). Also,
Discharge hole (11d) formed in the lower fixed scroll (11)
Has one end at the center of the lower working chamber (14) and the other end at the lower fixed scroll (11) lower casing internal space (B)
The refrigerant gas compressed in the lower working chamber (14) is discharged into the lower casing internal space (A).

The crankshaft (8) and each scroll (1
Bearing metal (17), (18), (19) is interposed between 0), (11) and (12). Specifically, as shown in FIG. 2, the eccentric part (8b) of the crankshaft (8) and the boss part (12e) of the orbiting scroll (12).
A cylindrical bearing metal (17) is interposed between the inner surface (center hole) and the crankshaft (8) and the fixed scrolls (10), (11) on both upper and lower sides of the bearing metal (17). Cylindrical bearing metals (18) and (19) are respectively interposed between and. Lubricating oil is supplied from the oil supply passage (8c) to the locations where the bearing metals (17), (18) and (19) are arranged.

Further, as shown in FIG. 1, the drive mechanism (4) is provided at the lower position of the lower fixed scroll (11) of the crankshaft (8).
A balancer (16) is provided to cancel the eccentric moment generated by the crankshaft (8) during rotation of the crankshaft to maintain a static balance, and the balancer (16 'for dynamic balance is provided at the upper end of the crankshaft (8). ) Is provided.

Further, at a plurality of positions near the outer peripheral edge of each scroll (10), (11), (12), a rotation for preventing rotation of the orbiting scroll (12) and performing a predetermined revolution motion is performed. A prevention member (15) is installed. The rotation preventing member (15) is composed of coaxial parts and is rotatably inserted into the fixed scrolls (10), (11), and the rotation parts (15a), (15a) and the rotation parts (15a),
It is formed between (15a) and is integrally formed with a revolving part (15b) which is eccentric from the axis of the rotating parts (15a) and (15a) and penetrates the end plate (12a) of the revolving scroll (12). ing. Therefore, the orbiting part (15b) orbits together with the orbiting scroll (12) to prevent the orbiting scroll (12) from rotating.

The characteristic structure of this embodiment is the bearing structure in the thrust direction of the orbiting scroll (12). As shown in FIG. 2, the orbiting scroll (12) is integrally formed with a vertically extending flange (20) on the outer peripheral edge thereof. That is,
In the orbiting scroll (12), the upper and lower wraps (12b) and (12c) are not formed in the outer peripheral edge portion, and the outer peripheral edge portion has a circular shape in a plan view independent of the wraps (12b) and (12c). A flange (20) is formed. The height of the flange (20) is approximately the same as the distance between the end plates (10a) and (11a) of the fixed scrolls (10) and (11). Faces the end plates (10a), (11a) of the fixed scrolls (10), (11) in close proximity, and bearing metal (21), (21) as a bearing member is interposed in the gap. There is. Then, between the bearing metal (21), (21) and the fixed scroll (10), (11), for example, lubricating oil supplied from the oil supply passage (8c) to the scroll mechanism (3) or other oil supply is provided. It is lubricated by the lubricating oil supplied from the passage. Also this flange
A supply port (not shown) that allows introduction of the refrigerant gas into each of the working chambers (13) and (14) is formed in (20). In this way, the thrust bearing means (22) is constituted by the flange (20) and the bearing metals (21), (21).

Next, the compression operation of the scroll type fluid device (1) constructed as described above will be explained. Electric motor
When (7) is driven, the crankshaft (8) rotates around the shaft center (Q). At this time, the eccentric part (8b) is connected to the crankshaft (8).
It revolves around the axis (Q) of. Along with this, the eccentric part
The orbiting scroll (12) through which (8b) is inserted revolves around the fixed scrolls (10) and (11). Further, the orbiting scroll (12) does not rotate due to the rotation preventing member (15). Then, on the upper and lower sides of the end plate (12a) of the orbiting scroll (12), the contact points of the opposing laps (10b), (12b), (11b), (12c) move toward the center. With this movement, the working chambers (13) and (14) are contracted while moving spirally toward the center. By this series of operations, low-pressure refrigerant gas flows from the suction pipe (5) into the working chambers (13) and (14), is compressed and becomes high pressure, and is discharged to the center of the working chambers (13) and (14). After reaching, it passes through the discharge holes (10d), (11d), and is discharged from the discharge pipes (6a), (6b) through the casing internal spaces (A), (B).

Also, at the time of this compression operation, the oil supply pump (8a)
Lubricating oil pumped up by the bearing metal (17), (18), arranged around the crankshaft (8) through the oil supply passage (8c).
(19) It is supplied to the peripheral portion and lubricated so that the crankshaft (8) can smoothly rotate with respect to the scrolls (10), (11) and (12).

And, as a characteristic operation of this example,
This is a bearing function in the thrust direction of the orbiting scroll (12). That is, the load in the thrust direction acting on the orbiting scroll (12) due to the difference in the amount of fluid leakage from the working chambers (13) and (14) and the own weight of the orbiting scroll (12) The bearing structure is constituted by a flange (20) formed on the outer peripheral edge of (12) and a bearing metal (21). Also,
Lubrication oil is also supplied to the periphery of the flange (20) for lubrication.

As described above, according to the structure of this example, since the orbiting scroll (12) is integrally provided with the thrust direction bearing, the amount of fluid leakage from the working chambers (13) and (14) is reduced. The difference or the load in the thrust direction acting due to the weight of the orbiting scroll (12) can be surely received, the friction loss due to this load can be reduced, and the compressor efficiency can be improved. Further, in the configuration of this example, since the flange (20) is formed on the outer peripheral edge portion of the orbiting scroll (12), a relatively large bearing area can be secured, and the load can be reliably received even in the case of a large thrust load. You can

(Second Embodiment) Next, a second embodiment of the present invention will be described. This example is a modification of the thrust bearing, and the other structure is the same as that of the first embodiment described above, so only the thrust bearing will be described in this example.

As shown in FIG. 3 and FIG. 4, the thrust bearing means (22) of this embodiment has a boss portion (12) of the orbiting scroll (12).
It is composed of bearing metal (23), (23) as a ring-shaped bearing member arranged on both upper and lower end faces of e). That is, the eccentric part (8b) of the crankshaft (8) and the boss part of the orbiting scroll (12).
Bearing metal (17) that forms a radial bearing with (12e),
The bearing metals (23), (23) forming this thrust bearing are arranged in close proximity to each other.

According to such a structure, the thrust bearing structure can be arranged at a position close to the downstream end of the oil supply passage (8c) so that the lubricating oil can be reliably supplied and a sufficient supply amount can be obtained. be able to. Further, it is not necessary to increase the outer diameter of the orbiting scroll (12) as in the first embodiment described above, so that the device can be downsized.

(Third Embodiment) Next, a third embodiment of the present invention will be described. Since this example is also a modification of the thrust bearing, only the thrust bearing will be described.

As shown in FIG. 5, the downstream end of the oil supply passage (8c), which opens to the outer peripheral surface of the eccentric portion (8b) of the crankshaft (8), is
A supply groove (25) having a large opening area is formed. Further, in the portion of the inner peripheral surface of the boss portion (12e) of the orbiting scroll (12) facing the supply groove (25), a groove-like oil supply pocket (26) is similarly formed, In the boss (12e), this refueling pocket (26) and the boss (12e)
Is formed with an oil supply guide passageway (27) which communicates with the upper and lower end surfaces of the. This refueling guide passage (27) has a refueling pocket at one end.
(26) and the other end that extends to the outer peripheral side in the horizontal direction (2
7a) and a vertical part (27a) that branches vertically from the outer end of the horizontal part (27a) and each end opens at both upper and lower end faces of the boss part (12e).
b) consists of Further, each end of the vertical portion (27b) is formed to have a slightly large diameter. Also, a refueling pocket
(26) may be formed over the entire inner peripheral surface of the boss portion (12e), and further, the oil supply guide passages (27) are formed at a plurality of positions in the circumferential direction of the boss portion (12e). It is preferable. Thus, the thrust bearing means (22) is constructed.

Also, in this example, the eccentric part of the crankshaft (8) is
No bearing metal is provided between (8b) and the orbiting scroll (12).

With such a structure, in the bearing operation of this example, a part of the lubricating oil supplied from the oil supply passage (8c) is
The eccentric portion (8b) of the crankshaft (8) and the inner peripheral surface of the boss portion (12e) of the orbiting scroll (12) are inserted into the gap to lubricate the both. Further, other lubricating oil flows from the supply groove (25) into the refueling pocket (26) and the horizontal portion (27) of the refueling guide passageway (27).
It is supplied between the upper and lower end surfaces of the boss (12e) and the end plates (10a) and (11a) of the fixed scrolls (10) and (11) through a) and the vertical portion (27b) to lubricate them.

In this way, since the lubricating oil is supplied to the upper and lower end surfaces of the boss portion (12e) which is the thrust surface by the oil supply passage (8c), the lubricating oil can be reliably supplied to the thrust surface,
Since the high pressure oil is supplied to the thrust bearing surface, the reliability of the thrust bearing can be improved.

(Fourth Embodiment) Next, a fourth embodiment of the present invention will be described. Since this example is also a modification of the thrust bearing, only the thrust bearing will be described.

As shown in FIG. 6, in this example, a concave portion (29) is formed in the central portion of the surface of the end plates (10a), (11a) of the fixed scrolls (10), (11), and the concave portion (29) is formed. 29) with an annular permanent magnet (3
0) and (30) are arranged. In addition, this permanent magnet (30), (3
Permanent magnets (31), (31) are attached to the upper and lower end surfaces of the boss (12e) of the orbiting scroll (12) facing the (0). And, as the arrangement state of each magnet (30), (30), (31), (31),
The magnets (30) and (31) facing each other have the same poles facing each other so that a repulsive force acts on them. Thus, the thrust bearing means (22) is constructed.

According to this structure, the magnets (30), (3
1) The repulsive force of each other causes the orbiting scroll (12) to be placed in a floating state in the space formed between the fixed scrolls (10) and (11), so that thrust load is applied. However, since the contact force of the orbiting scroll (12) with respect to the fixed scrolls (10), (11) is sufficiently small, it is possible to reduce the friction loss between the scrolls without requiring lubricating oil.

Although the compressor for the refrigerator has been described in this example, the scroll type fluid device (1) of the present invention may be used for a vacuum pump, an expander or the like.

[0046]

As described above, according to the present invention, the following effects are exhibited. According to the invention described in claim 1, since the orbiting scroll is provided with the thrust bearing means for receiving the load in the thrust direction acting on the orbiting scroll, it is caused by the leakage of fluid from each working chamber or the own weight of the orbiting scroll itself. Thus, the thrust load acting on the orbiting scroll can be received, the friction loss between the scrolls due to the thrust load can be reduced, and the mechanical efficiency of the scroll fluid device can be improved.

According to the second aspect of the present invention, the thrust bearing means is provided on the flange that forms a gap between the end plate of the orbiting scroll and the end plate of the fixed scroll, and the gap between the flange and the end plate. Since the bearing member is provided, a relatively large bearing area can be secured, and even if the thrust load is large, the load can be reliably received, and the reliability of the thrust bearing can be improved.

According to the third aspect of the invention, the thrust bearing means is a bearing member provided between both end faces of the boss portion formed at the edge of the center hole of the orbiting scroll and the end plate of the fixed scroll. Since the bearing member can be disposed close to the oil supply passage, the lubricating oil can be reliably supplied to the bearing member without increasing the size of the device, and the device can be downsized. And the realization of thrust bearings can be achieved at the same time.

According to the fourth aspect of the present invention, the thrust bearing means is formed in the boss portion formed at the edge of the center hole of the orbiting scroll, and both end surfaces of the boss portion and the oil supply passage are communicated with each other. Since both ends of the boss and the end plate of the fixed scroll opposed to the ends are formed by oil supply guide passages for supplying and lubricating the lubricating oil from the oil supply passage, both end surfaces of the boss that are thrust surfaces are formed. Lubricating oil can be reliably supplied, and reliability of the thrust bearing can be improved.

According to the fifth aspect of the present invention, the thrust bearing means includes the first permanent magnets provided on both end surfaces of the boss portion formed at the edge of the center hole of the orbiting scroll, and both end portions of the boss portion. A state in which the orbiting scroll is floated between the fixed scrolls because it is composed of a second permanent magnet provided on the end plate of the fixed scroll facing the surface, and the permanent magnets are arranged so that their magnetic pole surfaces face each other. Even if a thrust load acts on the orbiting scroll, the contact force between the respective scrolls becomes sufficiently small, so that the friction loss between the scrolls can be reduced without requiring lubricating oil.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a shaft penetration type double-toothed scroll type fluid device according to a first embodiment.

FIG. 2 is a sectional view of a scroll mechanism in the first embodiment.

FIG. 3 is a view corresponding to FIG. 2 in the second embodiment.

FIG. 4 is a cross-sectional view around a boss portion of an orbiting scroll according to a second embodiment.

FIG. 5 is a sectional view of a peripheral portion of a boss portion in a third embodiment.

FIG. 6 is a view corresponding to FIG. 5 in the fourth embodiment.

[Explanation of symbols]

 (1) Scroll type fluid device (2) Closed casing (4) Drive mechanism (8) Crankshaft (8b) Eccentric part (8c) Lubrication passage (10) Upper fixed scroll (11) Lower fixed scroll (12) Orbiting scroll (10a), (11a), (12a) End plate (10b), (11b), (12b), (12c) Wrap (10c), (11c), (12d) Center hole (12e) Boss (13), (14) Working chamber (20) Flange (21), (23) Bearing metal (bearing member) (22) Thrust bearing means (27) Lubrication guide passage (30), (31) Permanent magnet

Claims (5)

[Claims] 1. A pair of spiral wraps (10b), (11b) provided upright on the front surfaces of the end plates (10a), (11a) and fixed to a casing (2) with the front surfaces facing each other. It is arranged between the fixed scrolls (10), (11) of each and each fixed scroll (10), (11), and the end plate (12
A spiral wrap (12b), (12c) is erected on both sides of (a), and each wrap (12b), (12c) is a fixed scroll (10), (11).
Of the working chambers (13) and (14) by meshing with the wraps (10b) and (11b), respectively.
The orbiting scroll (12) that forms the action chamber (12) and the orbiting scroll (12) revolves with respect to the fixed scrolls (10) and (11) by the rotation of the crankshaft (8) extending from the drive mechanism (4). In a scroll type fluid device in which the internal volumes of 13) and (14) are changed to compress the fluid, the orbiting scroll (12) is provided with a thrust load that acts on the orbiting scroll (12) in the thrust direction. Bearing means (2
2) A scroll type fluid device characterized by being provided. 2. The thrust bearing means (22) extends from the outer peripheral edge of the orbiting scroll (12) toward the end plates (10a), (11a) of the fixed scrolls (10), (11), and the end plates (10a). ), (11a) to form a gap between the flange (20) and the bearing member (21) disposed in the gap between the flange (20) and the end plates (10a), (11a). The scroll type fluid device according to claim 1, wherein the scroll type fluid device is formed. 3. The crankshaft (8) has a fixed scroll (1
0), (11) and the orbiting scroll (12) central holes (10c), (11c), (12d) are respectively inserted through the eccentric portion (8b) formed on the crankshaft (8) Center hole (1) of orbiting scroll (12)
2d), the crankshaft (8) is formed with an oil passage (8c) for supplying lubricating oil to the outer peripheral surface of the eccentric part (8b), and the thrust bearing means (22) is Both end faces of a boss (12e) formed at the edge of the center hole (12d) of the orbiting scroll (12) and the end plates (10) of the fixed scrolls (10), (11) facing the both end faces.
The scroll type fluid device according to claim 1, wherein the scroll type fluid device comprises a bearing member (23) interposed between a) and (11a). 4. The crankshaft (8) has a fixed scroll (1
0), (11) and the orbiting scroll (12) central holes (10c), (11c), (12d) are respectively inserted through the eccentric portion (8b) formed on the crankshaft (8) Center hole (1) of orbiting scroll (12)
2d), the crankshaft (8) has an oil passage (8c) for supplying lubricating oil formed through the outer peripheral surface of the eccentric portion (8b), and the thrust bearing means (22) is Center hole of orbiting scroll (12)
(12d) is formed on the boss (12e) formed on the edge of the boss (12e) so that both end surfaces of the boss (12e) and the oil supply passage (8c) are communicated with each other and both end surfaces of the boss (12e). Fixed scroll facing the surface
Characterized by an oil supply guide passage (27) for supplying and lubricating the lubricating oil from the oil supply passage (8c) between the end plates (10a) and (11a) of (10) and (11). The scroll type fluid device according to claim 1. 5. The crankshaft (8) has a fixed scroll (1
0), (11) and the orbiting scroll (12) central holes (10c), (11c), (12d) are respectively inserted through the eccentric portion (8b) formed on the crankshaft (8) Center hole (1) of orbiting scroll (12)
2d), the thrust bearing means (22) is provided on both end surfaces of the boss portion (12e) formed at the edge of the center hole (12d) of the orbiting scroll (12). The magnets (30), (30) and the end plates (10) of the fixed scrolls (10), (11) facing both end faces of the boss (12e).
a) and (11a) and second permanent magnets (31) and (31), and the permanent magnets (30) and (31) are arranged so that their magnetic pole faces face each other. The scroll type fluid device according to claim 1, wherein.