JPH03990A - Scroll type fluid device - Google Patents

Abstract

PURPOSE:To make back pressures act through the repelling forces of magnets so as to lessen the load of thrust by providing driving and driven scroll end plates and frames disposed at the back sides of the end plates, with the magnets, respectively. CONSTITUTION:End plate side magnets are, respectively, arranged on the back sides of end plates 31, 41 in driving and driven scrolls meshing with each other. Recesses 72 are, respectively, disposed on the positions in opposition to the magnets 71 of frames 5, 6, while in the recesses 72 frames side magnets 73 are, respectively fitted in, of which magnetic poles are different from the magnets 71. In the recesses 72 back pressure chambers 76 are, respectively, formed, in which high pressure or intermediate pressure is introduced in the portion between the bottoms and the magnets 73. The back pressures are applied to both scrolls through the repelling forces of both magnets 71, 73, thereby alleviating the load of thrust.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a double-rotating scroll-type fluid device used in a compressor, etc., and particularly relates to countermeasures against thrust loads between both scrolls and countermeasures against a coupling mechanism. It is something.

(Prior Art) In general, this type of double-rotating scroll compressor has spiral wraps erected on the front surface of each end plate, as disclosed in Japanese Patent Application Laid-open No. 191685/1985. At the same time, a driving scroll and a driven scroll, each having a driving shaft and a driven shaft connected to each other on the back side, are housed side by side in a sealed casing with their respective wraps meshing with each other, and the driving shaft and driven shaft are respectively connected to the back side of the end plate. Each scroll is rotatably fitted into a frame provided on the scroll and supported by the frame, and both scrolls are arranged such that the axes of the drive shaft and the driven shaft are spaced apart from each other by a predetermined distance. .

When the driving scroll rotates, the driven scroll rotates in synchronization with the rotation, and a sealed chamber is formed between the end plates by both wraps, and the sealed chamber moves toward the center and contracts. compresses the fluid.

(Issue 8 to be solved by the invention) In the scroll-type fluid device described above, the first problem is that since the fluid is compressed between the end plates of each scroll, a thrust load acts on each scroll. A thrust bearing is interposed between the frame and the thrust bearing to receive and stop the thrust load.

However, in the above-mentioned thrust bearing, since the end plate is in direct contact with the end plate, there is a large loss, and furthermore, the thrust load is large, so there is a problem that each scroll cannot be supported sufficiently. This thrust load is, for example, 1
Even those in the horsepower class have a power rating of about 130 kg-f, which poses a problem in that the reliability of support in the thrust direction is low.

In addition, the rotational speed of a double-system rotary type is high. For example, in a general orbiting scroll type fluid device, the orbiting scroll performs revolution operation with the radius of the base circle as the radius, and the sliding speed of the thrust bearing part is 1. Horsepower class 3600
In the rpm state, it is about 0.8 m/sec, whereas in the double-system rotary type, each scroll rotates on its own axis, so in the 1 horsepower class type, the speed is 360 O
At rpm, the sliding speed of the thrust bearing is 9
, about 5 m/sec, which is about 12 times as large. Furthermore, we aim to increase the rotation speed of each scroll to 20,000 r.
When trying to rotate at pm, the sliding speed is 52m/sec.
c (approximately 65 times), and the reliability of the thrust bearing becomes a problem.

Therefore, as disclosed in Japanese Unexamined Patent Publication No. 58-110885, there is a system in which the high-pressure fluid between both scrolls is guided to the back side of each scroll to directly apply back pressure. To seal against back pressure, a high-speed sliding seal must be provided between each scroll and the frame, and this sliding seal is extremely difficult to lubricate due to the high-speed contact between each scroll. . In addition, as disclosed in Japanese Patent Application Laid-open No. 59-15690, there is a double-toothed scroll that structurally reduces the thrust load to zero, but the drive mechanism becomes extremely complicated. There is a problem.

In addition, as a second problem, the connection between the driving scroll and the driven scroll is such that the outer circumferential side and the inner circumferential side of the wraps of both scrolls contact each other at multiple points, and the driven scroll or the driving scroll is connected via the wraps. It rotates according to the rotation of.

However, since rotational force acts on both wraps, sufficient strength is required in this case, and the wraps are also prone to wear, which causes transmission loss of rotational force and changes in the contact points between both wraps. However, there were problems such as noise generation.

Furthermore, it is conceivable to provide an Oldham joint between the driving scroll and the driven scroll, but since the Oldham joint moves in a circular orbit with a diameter between the rotation centers of both scrolls, vibrations may occur. And, moreover,
In order to balance the eccentric motion, a balance weight must be provided, which poses a problem of complicating the structure.

The present invention has been made in view of these points, and aims to reduce thrust load to reduce loss, improve reliability, and improve power transmission between both scrolls. The purpose is to

(Means for Solving the Problems) In order to achieve the above object, the first means taken by the present invention is to reduce the thrust load by utilizing the repulsive force of the magnet.

Specifically, as shown in FIG. 1, the means taken by the invention according to claim (1) are as follows:
Swirled wrap (32) on the front of the.

(42) is erected, and a drive shaft (33) and a driven shaft (43) are connected to the back surface.
) and a driven scroll (4) each wrap (32),
(42) are meshed with each other and arranged side by side in the casing (2), and the drive shaft (33) and driven shaft (43) are arranged so that their axes are spaced apart from each other by a predetermined distance. It is fitted into the frames (5) and (6) provided on the side, and the back side of each frame (5) and (6) is a high pressure chamber (2a),
In (2b), a low pressure chamber (23) is formed between the frames (5) and (6), so that the driven scroll (4) rotates in synchronization with the rotation of the drive scroll (3). The target is scroll-type fluid devices.

Magnets (71), (71) are provided on the back surfaces of each of the mirror plates (31), (41), while recesses (72) are provided in each of the frames (5), (6).

(72) are formed at positions facing the end plate side magnets (71), (71), and the recesses (72), (72)
In this case, the distance between the magnets (73) (73) whose opposing surfaces are set to different magnetic poles from the end plate side magnets (71) and (71) is changed. It is fitted so that it can slide freely. Furthermore, the recess (72)
, (72) includes a back pressure chamber (76) in which high pressure or intermediate pressure is introduced between the bottom of the recess (72), (72) and the frame side magnet (73), (73). 76) is formed.

Further, the means taken by the invention according to claim (a) is the invention according to claim (1), in which at least both end plate magnets (
Either the magnet (71) or the frame-side magnet (73) is configured to have a donut plate shape.

In order to achieve the above-mentioned other objects, another means taken by the present invention is that the end of the connecting pin and the end plate are brought into rolling contact to maintain a good lubrication state. It is.

Specifically, as shown in FIG. 3, the measures taken by the invention according to claim (3) are first aimed at the scroll-type fluid device to which the invention according to claim (1) is directed. Both scrolls (3) are arranged so that the driven scroll (4) rotates in synchronization with the rotation of the driving scroll (3).
(4), the connecting means (8) that connects both mirror plates (31
), (41), and the end of the connecting pin (81) formed on the front outer periphery of the other mirror plate (41) is engaged. The roller (83) is rotatably provided at the end of the connecting pin (81) and rolls in contact with the side surface of the engaging recess (82).

Moreover, the means taken by the invention according to claim (4) is such that in the inventions according to claims (1) and (2), the connecting means (8) of the invention according to claim (3) is provided.

(Function) With the above configuration, in the inventions according to claims (1) and (2), when the drive shaft (33) is rotated, the drive scroll (33) is rotated.
) rotates, and the rotation of the driving scroll (3) causes the driven scroll (4) to rotate synchronously. Specifically, in the inventions of claims (3) and (4), the driving scroll (3)
The connection pin (81) rotates due to the rotation of the connection pin (81), and the connection pin (81) rotates.
The engagement recess (
The roller (83) rolls inside the drive scroll (
The rotational force of 3) is transmitted to the driven scroll (4), and the driven scroll (4) rotates in synchronization with the driving scroll (3).

Due to the rotation of both scrolls (3) and (4), a sealed chamber (13) is formed between both wraps (32) and (42), and the sealed chamber (13) is moved toward the center, for example. It contracts while compressing the fluid.

On the other hand, although a thrust load acts on each of the scrolls (3) and (4), the back pressure chamber (
A high-pressure or intermediate-pressure fluid flows into 76) to move the frame side magnet (73) close to the end plate side magnet (71).

The above-mentioned back pressure is applied to each scroll (3) through the repulsive force of (73).
), (4), and the thrust load is offset or reduced by the back pressure.

(Effect of the invention) Therefore, according to the inventions of claims (1) and (4),
Since back pressure is applied to each scroll (3), (4) through the repulsive force of two magnets (71), (73), each scroll (3), (4) is supported without contact. Alternatively, the thrust load can be significantly reduced, so that the loss caused by the conventional thrust bearing can be reduced with a simple drive mechanism. In particular, since high-pressure fluid is not applied directly to the back side of each scroll (3), (4), sliding seals are not required, and in a double-system rotary type with high rotation speed, each scroll (3), (4) contact loss can be significantly reduced, each scroll (3) (
4) It is possible to improve the reliability of supporting.

Furthermore, in the inventions according to claims (2) and (4), since only one of the two opposing magnets (71) and (73) is formed into a donut plate shape, both of them are formed into a donut plate shape. The amount of materials used can be reduced compared to other methods, and the cost can be reduced.

Further, according to the inventions according to claims (3) and (4), the engagement recess (82) and the roller (83) roll into contact to connect both scrolls (3) and (4). , the connecting pin (81), the roller (83) and the engaging recess (
82) can be maintained in a good lubrication state, and loss due to contact can be reduced.

Moreover, the sliding speed between the connecting pin (81) and the roller (83) can be reduced, and the rotational force of the driving scroll (3) can be reliably transmitted to the driven scroll (4), so power transmission Efficiency can be improved, and at the same time, the driven scroll (4) can be accurately rotated synchronously with the driving scroll (3).

Further, since the rotational force is not transmitted through both the wraps (32) and (42) as in the conventional case, the wraps (32) and (42)
The strength of (42) can be reduced, wear can be reduced, and generation of vibration can be suppressed.

Further, unlike a conventional Oldham joint, the connecting pin (81) rotates, so dynamic balance can be easily maintained and vibrations can be reduced.

(Example) Hereinafter, an example of the present invention will be described in detail based on the drawings.

As shown in FIG. 1, (1) is a double-rotating scroll type fluid device, which is used as a compressor in a refrigeration system to compress and discharge refrigerant gas.

The scroll type fluid device (1) has a closed casing (2)
A scroll mechanism (11) is housed inside the scroll mechanism (11), and a drive motor (12) is housed therein.
11) is a driving scroll (3) and a driven scroll (4)
are supported by frames (5) and (6), respectively. Both frames (5) and (6) are formed in a substantially disk shape, and each of the scrolls (3) and
(4) are provided in parallel with a predetermined interval so as to be located on the back side. And both frames (5),
(6) is fixed to the casing (2) on the outer peripheral surface,
Shaft holes (51), (61) for rotatably supporting each of the scrolls (3), (4) are vertically bored in the center, and the two wheel holes (51), (61) are connected to the shaft. The cores are formed at predetermined intervals in the radial direction.

Both scrolls (3) and (4) have a wrap (32) formed in an involute shape on the front surface of an end plate (31), (41) formed in a disk shape.
42) are arranged upright, and both mirror plates (31),
(41) with the front faces of both frames (5) facing each other.
), (6), and each of the above wraps (
32) and (42) are meshed with each other. Furthermore, a drive shaft (33) is attached to the back (lower surface) of the end plate (31) of the driving scroll (3), and a drive shaft (33) is attached to the end plate (31) of the driven scroll (4).
4) Driven shafts (43) are connected to each other on the back (top surface), and the drive shafts (33) and driven shafts (43) are connected to the shaft holes (51), ( 61) via radial bearings (34) and (44) so as to be rotatable. Further, thrust support means (7) for receiving and receiving thrust loads is interposed between each of the end plates (31) and (41) and each of the frames (5) and (6), and each of the scrolls (3 )(4th frame is frame (5), (
6) is supported. The drive shaft (33) extends to the bottom of the casing (2) and is fitted into the rotor (12a) of the drive motor (12), and the stator (12b) of the drive motor (12). is fixed to the casing (2).

Further, the driving shaft (33) and the driven shaft (43) are provided so that the driving shaft center (01) and the driven shaft center (02) are eccentric to each other with a predetermined interval in the radial direction. Following the rotation of the driving scroll (3), the driven scroll (4) rotates synchronously via the connecting means (8), so that one scroll (3) or (4) is relatively connected to the other scroll (4) or (3). It is configured to only revolve around.

On the other hand, the tip surfaces of each of the wraps (32) and (42) are in contact with the end plates (31) and (41) facing each other, and the inner and outer circumferential surfaces are in contact at multiple points, and the area between these contacts is the closed chamber. (13), and the sealed chamber (13) is configured to contract while moving toward the center of both scrolls (3) and (4).

Inside the casing (2), the upper side of the frame (6) is defined by the driven frame (6), and the lower side of the frame (5) is defined by the drive side frame (5) as high pressure chambers (2a), (2b).
), and the art commercial pressure chamber (2a), (
2b) is both frames (5).

(6) is communicated by a through passage (2C) bored therein. In addition, a suction pipe (
21) is connected to the high pressure chamber (2a) and has a discharge pipe (
22) are connected to each other. And a wrap (32) between the above frames (5) and (6),
The outside of (42) is formed into a suction chamber (23) which is a low pressure chamber, and the suction pipe (21) is communicated with the suction chamber (23), and the low pressure refrigerant gas introduced from the suction pipe (21) is connected to the suction chamber (23). The air is configured to flow into the sealed chamber (13) from the suction chamber (23). Furthermore, the driven scroll (4) has a discharge passageway (45) in the center that runs from the front of the end plate (41) to the driven shaft (4).
43) is perforated across the end surface (upper surface) of the sealed chamber (
13) The high pressure refrigerant gas is configured to flow out into the high pressure chamber (2a). Furthermore, the above casing (2)
The bottom of the interior is an oil reservoir (24) for lubricating oil, in which the lower end of the drive shaft (33) is immersed, and although not shown, lubrication is carried out through an oil supply path provided on the drive shaft (33). Oil is supplied to the radial bearings (34) and the like.

On the other hand, as shown in FIG. 2, the thrust support means (7), which is one of the features of the present invention, includes both scrolls (3),
The end plate side magnets (71), (71) provided on the end plate (31), (41) of (4), both frames (5),
It is composed of frame-side magnets (73) and (73) provided in the recesses (72) and (72) of (6). The end plate side magnet (71) is formed in the shape of a donut plate, and is connected to each end plate (31).

(41) (lower surface for driving scroll (3), upper surface for driven scroll (4)), and the axis (0+) of each driving shaft (33) or driven shaft (43),
(02), each end plate (31), (4
1) is provided flush with the back surface of 1).

Further, the recessed portion (72) is provided in each frame (5).

(6) (the surface facing the end plate (31), (41)), is located opposite to the end plate side magnet (71), and is located on the drive shaft (33) or driven shaft ( 43) and is formed in a ring shape concentrically with the U-shaped cross section (second
It is formed into an inverted U-shape (in the figure). Furthermore, each of the above frames (5) and (6) includes the frame (5) and (
6) (hyperpressure chamber (2a), (2b) side) and recess (7)
A communication passage (74) is bored in the bottom of the recess (72), and the high pressure chambers (2a), (2b) are formed in the recess (72).
The high-pressure refrigerant gas is introduced.

Further, the frame side magnet (73) is formed into a donut plate shape corresponding to the recess (72), is inserted into the recess (72), and is provided facing the end plate side magnet (71). There is. Further, the frame side magnet (73) is provided with a magnetic pole having a facing surface different from that of the end plate side magnet (71), and is set so that a repulsive force is generated between the frame side magnet (73) and the end plate side magnet (71). At the same time, it is fitted into the recess (72) so as to be slidable in the vertical direction so that the distance from the end plate side magnet (71) changes. An O-ring (75) is interposed between the side surface of the recess (72) and the side surface of the frame-side magnet (73) to provide a seal, and the bottom surface of the recess (72) and the side surface of the frame-side magnet (73) are sealed. A back pressure chamber (76) is formed between the back pressure chamber (76) and the back pressure (F bp) of the back pressure chamber (76) and both magnets (71).

The thrust load (F su) of each scroll (3), (4) is canceled out by the repulsive force (F mg) of (73) without contact.

In other words, the repulsive force (F
mg) is inversely proportional to the square of the distance (spacing) between both magnets (71) and (73), so back pressure (F
bp) does not act, the frame side magnet (73) sinks into the recess (72) and the frame side magnet (73) sinks into the recess (72) and the frame side A magnet (73) is set. Then, back pressure (F bp) is applied to the frame side magnet (73).
acts, the back pressure (F bp) and repulsive force (F mg
) The frame side magnet (73) moves within the recess (72) so that the back pressure (F bp) is balanced with the magnet (71
).

(73) to each scroll (3), (4). Furthermore, the above-mentioned back pressure (F b
p) is set to be equal to the thrust load ff1 (Fsu), and each scroll C3), (4) is configured to be supported by the frames (5), (6) in a non-contact manner. In addition, if the back pressure (F bp) is smaller than the thrust load (F su), each scroll (3
), (4) are in contact with the frames (5), (6), but the thrust load (F su) is reduced. still,
The back pressure (F bp) is set so as not to be greater than the thrust load (FSU), and is configured so that no reverse thrust load acts.

Further, the above-mentioned connecting means (8) which is one of the other features of the present invention
), as shown in Figures 3 and 4, each scroll (3
), (4), a plurality of connecting pins (81), (81), . . . are sunk between the end plates (31), (41). The connecting pin (81) has a large diameter portion (
A small diameter part (81b) is connected to the upper end of 81a),
The height of the large diameter portion (81a) is equal to that of both mirror plates (31) and (41).
The lower end of the large diameter portion (81a) is fixed to the front outer peripheral edge of the end plate (31) of the drive scroll (3), and the connecting pin (81
) has been erected. On the other hand, the above-mentioned driven side scroll (4
), a connecting pin (8
An engagement recess (82) is formed corresponding to the small diameter portion (81b) of 1), the engagement recess (82) is formed in a circular recess, and a connecting pin is inserted into the engagement recess (82). The small diameter portion (81b) of (81) is configured to be inserted.

Further, a roller (83) is fitted onto the small diameter portion (81b) of the connecting pin (81), and the roller (83) is rotatably provided in the small diameter portion (81b) and has an outer peripheral surface. The engagement recess (82) is in contact with the side surface of the engagement recess (82).
2) It is configured to roll within. The engagement recess (82) is formed so that its diameter (D) satisfies the following formula, D-d+2e...■ d: Diameter e of the roller (83): Drive shaft (33) and driven Amount of eccentricity with respect to the shaft (43) While the roller (83) rolls in the engagement recess (82), the rotational force of the drive scroll (3) is transmitted to the driven scroll (4). ) drives the scroll (
4) is configured to rotate in synchronization with. Also,
Although not shown, oil supply holes are formed in the connecting pin (81) and the roller (83), and the drive scroll (3
) is configured so that lubricating oil is supplied through the end plate (31) and the like.

Next, the compression operation of this scroll type fluid device (1) will be explained.

First, when the drive motor (12) is driven to rotate the drive shaft (33), the drive scroll (3) rotates around the axis (01) of the drive shaft (33), and the end plate (31) rotates. Therefore, the connecting pin (81) also rotates around the drive shaft center (01). The rotation of the connecting pin (81) transmits the rotational force of the driving scroll (3) to the driven scroll (4), and at this time, the roller (83) moves into the engagement recess (82).
The engagement recess (82) rolls in contact with the side surface of the engagement recess (82).

The rotation of this connecting pin (81) causes the driven scroll (4
) rotates, and the driven scroll (4) rotates in synchronization with the driving scroll (3), and according to this synchronous rotation, one scroll (3) or (4) rotates with respect to the other scroll (4). Or (3) will only perform relative revolution. Along with this revolution, wrap (32), (4
2) moves toward the center, and the sealed chamber (13) between the wraps (32) and (42) moves toward the center.
) (42), and the sealed chamber (13) contracts while moving spirally toward the central discharge passageway (46).

On the other hand, low-pressure refrigerant gas is supplied from the suction pipe (21) to the casing (
2) into the suction chamber (23) in the sealed chamber (13).
flows into. Then, due to the contraction of the sealed chamber (13), the low pressure refrigerant gas is compressed and becomes high pressure refrigerant gas, and the high pressure refrigerant gas passes through the discharge passageway (45), flows into the high pressure chamber (2a), and then flows through the discharge pipe ( 22).

On the other hand, both scrolls (3) and (4) are subjected to vertical thrust loads (F) due to the compressed refrigerant gas.
su) will act, and the thrust load (F s
As shown in FIG. 2, u) is canceled out or reduced by the back pressure (Fbp) and the repulsive force (F mg) of both magnets (71) and (73). That is, when the high pressure chambers (2a) and (2b) are not filled with high pressure refrigerant gas, such as during startup, high pressure refrigerant gas is not introduced into the back pressure chamber (76), so the frame side magnet (73) The recess (72) is created by the repulsive force (F mg) with the end plate side magnet (71).
Move to the bottom side (upper side in Figure 2) of each scroll (
3) No reverse thrust load acts on (4).

After that, the compression operation progresses, and each high pressure chamber (2a) (2b)
becomes a high-pressure atmosphere, high-pressure refrigerant gas flows into the back pressure chamber (76).
is introduced into the frame side magnet (73), and the back pressure (F bp
) acts to move closer to the end plate side magnet (71). This movement of the frame side magnet (73) causes the end plate side magnet (71
) and the repulsive force (F IIlg) changes, and this repulsive force (
F mg) is inversely proportional to the square of the distance (spacing), and the back pressure (F bp) is transmitted to each scroll (3), (4) via this repulsive force (F ff1g). Then, due to this back pressure (F bp), each scroll (3), (
4) to frame (5).

(6) If the thrust load (F su) that presses on the frame (F su) is canceled out and this back pressure (F bp) is matched with the thrust load (F su), each end plate (31), (41) Each of the scrolls (3) and (4) is supported without contacting the scrolls (3) and (6).

In addition, when the back pressure (F bp) described above decreases or the thrust load (F su) increases, the end plate side magnet (71
) will be close to the frame side magnet (73),
The repulsion force (F mg) increases and the frame side magnet (7
3) will escape in the direction of separation, and the reverse thrust load will not act on each scroll (3) and (4). At that time, each end plate (31), (41) is a frame (5)
, (6), but the thrust load (F
su) will be reduced.

Therefore, back pressure (F bp) is applied to each scroll (3) through the repulsive force of the two magnets (71), (73).

(4), each scroll (
3) Is it possible to support (4) without contact?
Alternatively, since the thrust load can be significantly reduced, the loss caused by conventional thrust bearings can be reduced with a simple drive mechanism.

In particular, since high-pressure refrigerant gas is not applied directly to the back side of each scroll (3), (4), sliding seals are not required, and high rotational speeds (for example, 200
0 Orp) Each scroll (3) in both systems rotary type
, (4) can be significantly reduced, and the reliability of supporting each scroll (3) and (4) can be improved.

In addition, since the engagement recess (82) and the roller (83) roll into contact to connect both scrolls (3) and (4), the connection bin (81), the roller (83) and the engagement recess (82), it is possible to maintain a good lubrication state between each other, and it is also possible to reduce loss due to contact. Moreover, the sliding speed between the connecting bin (81) and the roller (83) can be reduced, and the driving scroll (
3) can be reliably transmitted to the driven scroll (4), improving power transmission efficiency and at the same time accurately synchronizing the driven scroll (4) with the driving scroll (3). It can be rotated.

Further, since the rotational force is not transmitted through both the wraps (32) and (42) as in the conventional case, the wraps (32) and (42)
The strength of (42) can be reduced, wear can be reduced, and generation of vibration can be suppressed.

Furthermore, unlike the conventional Oldham joint, the connecting pin (81) rotates, so dynamic balance can be easily maintained and vibrations can be reduced.

FIGS. 5 and 6 show other embodiments. In the one shown in FIG. 5, the height of the connecting bin (84) is shortened, and the power transmission between both scrolls (3) and (4) is reduced. Rap (32)
, (42) is performed at approximately the center in the height direction.

That is, a flange portion (46) projecting downward is formed on the front outer peripheral edge of the end plate (41) of the driven scroll (4), and an engagement recess (82) is formed in the flange portion (46). As in the previous embodiment, a connecting pin (84) is engaged with the engagement recess (82) via a roller (83) to transmit the rotational force of the driving scroll (3) to the driven scroll (4). are doing. Other configurations, functions, and effects are the same as in the previous embodiment.

Furthermore, the one shown in FIG. 6 is constructed so that intermediate pressure refrigerant gas is introduced into the back pressure chamber (76).

That is, each scroll (3), (4) has a first introduction path (77), (77), and each frame (5) has a first introduction path (77), (77).

(6) is formed with second introduction passages (78) and (7g), respectively, and the negative end of the first introduction passage (77) opens at the front of each end plate (31) and (41). It is formed so as to communicate with the sealed chamber (13) in which the refrigerant gas is compressed to an intermediate pressure, and passes through the head plate (31) (41) and the drive shaft (33) or the driven shaft (43), and the other end Shaft hole (51
), (61) are formed in the annular spaces (52), (6
2). On the other hand, the second
The introduction path (78) has one end connected to the annular spaces (52) and (62).
), the other end is formed in communication with the back pressure chamber (76).

Therefore, the intermediate pressure refrigerant gas is introduced into the back pressure chamber (76) via the first introduction path (77) and the second introduction path (78), and this intermediate pressure back pressure (F b p) The frame side magnet (73) acts. The other configurations, actions, and effects are the same as in the previous embodiment.

In each example, the magnets (71) and (73) were all formed in the shape of a donut plate, but only one of the magnets (71) and (73) on the end plate side or the frame side was formed in the shape of a donut plate. On the other hand, a plurality of small magnet pieces may be provided. This makes it possible to reduce the amount of materials used and to manufacture the device at low cost.

Further, the connecting means (8) may be configured by forming an engaging recess (82) in the driving scroll (3) and providing connecting pins (81) and (84) in the driven scroll (4).

Further, although the scroll type fluid device (1) of this embodiment was used as a compressor in a refrigeration system, the present invention may be applied to other compressors, expanders, etc.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention, and FIG. 1 is a longitudinal sectional view of a scroll-type fluid device. FIG. 2 is an enlarged sectional view of the thrust support means, FIG. 3 is an enlarged sectional view of the connecting means, and FIG. 4 is a plan sectional view thereof. FIG. 5 is an enlarged sectional view of a connecting means showing another embodiment, and FIG. 6 is an enlarged sectional view showing another embodiment of the thrust support means. (1)...Scroll type fluid device (2a), (2b)...High pressure chamber (3)...Drive scroll (4)...Followed scroll (5), (6)...Frame ( 7) Thrust support means (8) Connection means (23) Suction chambers (31), (41) End plate (32), (42) Wrap (33) ... Drive shaft (43) ... Driven shaft (71), (73) ... Magnet (72) ... Recess (81), (84) ... Connection pin (82) ...
Engagement recess (83)...Roller

Claims (1)

[Claims] (1) Spiral wraps (32), (42) are provided in front of the end plates (31), (41) respectively, and a drive shaft (33) and a driven shaft ( A driving scroll (3) and a driven scroll (4) are arranged in parallel in the casing (2) with the respective wraps (32) and (42) being engaged with each other, and the driving shaft (33) and the driven scroll (4) are connected to each other. The driven shaft (43) is connected to the mirror plates (31) and (41) so that the shaft centers are spaced apart from each other by a predetermined distance.
It is fitted into the frames (5) and (6) provided on the back side, and the back side of each frame (5) and (6) is connected to the high pressure chamber (2a
) and (2b), a low pressure chamber (23) is formed between the frames (5) and (6), and the drive scroll (3
) is a scroll-type fluid device in which a driven scroll (4) rotates synchronously with the rotation of
, (71), while each of the above frames (5),
(6) has recesses (72), (72) on the end plate side magnet (
71) and (71), and the recess (
72), (72) are the end plate side magnets (71), (71).
) with the opposing surface set to a different magnetic pole (73)
, (73) are slidably fitted in such a manner that the distance from the end plate side magnets (71), (71) changes. 72) and the frame side magnet (73),
(73) A back pressure chamber (
76), (76) are formed. (2) The scroll type fluid device according to claim (1), wherein at least one of the end plate side magnet (71) or the frame side magnet (73) is formed in a donut plate shape. Fluid equipment. (3) Spiral wraps (32), (42) are erected on the front surfaces of the end plates (31), (41), respectively, and a drive shaft (33) and a driven shaft (43) are connected to the back surfaces. A driving scroll (3) and a driven scroll (4) are arranged side by side in the casing (2) with their respective wraps (32) and (42) meshing, and the driving shaft (33) and driven shaft (43) are The end plates (31) and (41) are arranged so that the axes are spaced apart from each other by a predetermined distance.
Both scrolls (4) are fitted into frames (5) and (6) provided on the back side so that the driven scroll (4) rotates synchronously with the rotation of the drive scroll (3).
3), a scroll-type fluid device provided with a connecting means (8) for connecting the end plates (31) and (4), wherein the connecting means (8) is located outside the front surface of either one of the end plates (31), (41). A connecting pin (81) is provided upright on the peripheral edge, and an engagement recess (8
2), and a roller (8) which is rotatably provided at the end of the connecting pin (81) and rolls in contact with the side surface of the engagement recess (82).
3) A scroll-type fluid device comprising: (4) In the scroll type fluid device according to claim (1) or (2), there is a gap between the driving scroll (3) and the driven scroll (4) as the driving scroll (3) rotates. A connecting means (8) is provided for connecting both scrolls (3), (4) so that scrolls (4) rotate synchronously, and the connecting means (8) connects both end plates (31), (41
) A connecting pin (8
1), an engagement recess (82) formed on the front outer peripheral edge of the other mirror plate (41) and into which the end of the connecting pin (81) engages, and an engaging recess (82) that is rotatably formed at the end of the connecting pin (81). A scroll type fluid device comprising a roller (83) that is provided and rolls in contact with a side surface of an engagement recess (82).