JPH03260385A - Scroll type fluid device - Google Patents

Abstract

PURPOSE:To attain transmission of power, suited for a high rotational speed, by constituting a connecting means, which synchronously rotates a driven scroll with a drive scroll according to its rotation, of a plurality of drive and driven side engaging members formed in the peripheral edge of each end plate and engaged with each other. CONSTITUTION:Drive and driven scrolls 3, 4, formed by vertically providing spiral-shaped laps 32, 42 in the front surface of end plates 31, 41 in a scroll type fluid device 1, are meshed with each other, so that the driven scroll 4 is synchronously rotated with the drive scroll 3 according to its rotation by a connecting means 7. Here the connecting means 7 is constituted of a plurality of drive and driven side engaging members 71, 72 formed in the peripheral edge of each end plate 31, 41 and engaged with each other. Each side surface in normal/reverse rotational directions of each scroll 3, 4 in both the engaging members 71, 72 is curved in a centrifugal direction of the end plates 31, 41 and further formed in the first and second curved surfaces 73, 75;74, 76 contact- slidably opposed to each other between both the engaging members 71, 72.

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 or the like, and particularly relates to a coupling mechanism for both scrolls.

(Prior Art) In general, this type of double-rotary scroll compressor includes
A spiral wrap is erected on the front of each end plate, and
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 each provided on the back side of the end plate. Each scroll is rotatably fitted to the frame 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 an action chamber is formed between the end plates by both wraps, and the action chamber contracts while moving toward the center. compresses the fluid.

(Problems to be Solved by the Invention) In the scroll-type fluid device described above, two U-shaped connecting arms are attached to the end plate of the driven scroll, while
A joint having four guide grooves in orthogonal directions is provided on the rear surface of the end plate of the drive scroll and engages with two keys. The end of the connecting arm is engaged with the guide groove of the joint to connect both scrolls, so that the driven scroll rotates in accordance with the rotation of the driving scroll.

However, since the joint of the Oldham mechanism reciprocates according to the key and the connecting arm, it rotates and revolves, making it difficult to maintain balance and making it unsuitable for high-speed rotation.

Is it possible to consider using a ball joint or pin joint? Since this ball joint is provided on the outer periphery of the end plate, the turning radius is large, making it unsuitable for high speeds, and it also has multiple balls and guide holes. There is a problem that a retainer and the like are required, which increases the number of parts. In addition, since the pin joint rotates together with each scroll, it is excellent in terms of inertia, but since the pin radius is small, the pin joint has a problem in that it hits the sliding part harshly and is prone to wear. There is also the problem that increasing the pin radius increases the size of the entire device.

The present invention has been made in view of the above problems, and is designed to perform power transmission suitable for high-speed rotation, and to prevent abnormal contact between the laps during a stoppage or the like.

(Means for Solving the Problems) In order to achieve the above object, the means taken by the present invention is such that a plurality of driving side engaging members and driven side engaging members are arranged on both sides of the forward rotation side and the reverse rotation side. so that they touch each other.

Specifically, as shown in FIGS. 1 and 2, claim (1)
The measures taken by the invention according to ) first include a drive scroll (3) comprising a spiral wrap (32) erected on the front surface of an end plate (31) and a drive shaft (33) connected to the back surface;
A driven scroll (4) comprising a spiral wrap (42) erected on the front side of the end plate (41) and connected to a driven shaft (43) on the back side, each wrap (32), (42)
The target is scroll-type fluid devices that are installed in parallel.

A connecting means (7) is provided for connecting both scrolls (3) and (4) so that the driven scroll (4) rotates in synchronization with the rotation of the driving scroll (3). The means (7) includes each of the above end plates (31),
It is composed of a plurality of drive-side engagement members (71) (71), . . . and driven-side engagement members (72), (72), which are formed on the outer peripheral edge of (41) and engage with each other. There is. Furthermore,
The respective side surfaces of the scrolls (3) and (4) in the normal rotation direction and the reverse rotation direction in the two mating members (71) and (72) are curved in the centrifugal direction of the end plates (31) and (41), and The members (71) and (72) are formed into first curved surfaces (73), (75) and second curved surfaces (74), (76) that face each other so that they can slide into contact with each other. In addition, the first curved surface (73), (75) and the second curved surface (74)
, (76) is one of the first and second curved surfaces (75),
The other first and second curved surfaces (73) and (74) are formed so as to be located on the envelope of the closed curve of which (76) is a part.

Moreover, the means taken by the invention according to claim (2) is the first curved surface (73) (7
5) and the second curved surfaces (74), (76), one of the first and second curved surfaces (75), (76) is formed by a circular arc with a predetermined radius of curvature r, and the other first and second curved surfaces (75), (76) are
The curved surfaces (73) and (74) have a radius of curvature r1 of approximately "1 R:+R", where Ro is the amount of eccentricity between the drive shaft (33) and the driven shaft (43).

The structure is formed by a circular arc.

Further, the means taken by the invention according to claim (3) is that in the invention according to claim (1) or (2), both mating members (71a) and (71b) are formed to have the same shape in plan view. The structure is as follows.

In addition, the measures taken by the invention according to claim (4) are as follows in the invention described in claim +1), (2) or (3)
One engagement member (72b) is formed by a pin that is erected on the outer peripheral edge of the end plate (41) and protrudes toward the end plate (31) facing oppositely.
1) is formed on the outer peripheral edge.

Moreover, the means taken by the invention according to claim (5) is applied to the front outer peripheral edge of at least one end plate (31) in the invention according to any one of claims (1) to (4). The ring member (77a) faces the mirror & (41)
One engagement member (71c) is formed in the ring member (77a), and a flow path (78) through which fluid passes extends spirally from the outer peripheral surface to the inner peripheral surface. It has a formed configuration.

Moreover, the means taken by the invention according to claim (6) is the invention according to any one of claims (1) to (5) above, in which the means taken are in contact with the back side of one end plate (41). A thrust bearing (8) is provided, and the thrust bearing (8) is fixed to an engagement member (71) provided on the other end plate (31).

(Function) With the above configuration, in the invention according to claims (1) to (4), when the drive fill (33) is rotated, the drive scroll (3) is rotated and the drive side engagement member (71) is rotated. .

Then, the first curved surface (73) of any one of the driving-side engaging members (71) is in contact with the first curved surface (75) of any of the driven-side engaging members (72). As a result, the driven-side engaging member (72) rotates, and the rotational force of the driving scroll (3) is transmitted to the driven scroll (4), causing the driven scroll (4) to rotate.

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

Furthermore, the second curved surfaces (74) and (76) of either of the engaging members (71) and (72) are in contact with each other,
As the first curved surfaces (73) and (75) come into contact, the relative angle between both scrolls (3) and (4) is maintained, and the speed of the driven scroll (4) decreases as the drive scroll (3) decelerates, etc. do.

In addition, in the invention according to claim (5), the fluid flows through the flow path (7).
8), and flows into or out of the action chamber (13), and kinetic energy, for example, centripetal force, is obtained when flowing through this flow path (78).

Further, in the invention according to claim (6), both scrolls (3
), the thrust force in the opposite direction generated in (4) is 1
The bearing is stopped by two thrust bearings (8).

(Effect of the invention) Therefore, according to the inventions according to claims (1) to (4), a plurality of engaging members (71,), (72) are provided on both scrolls (3), (4), 1 curved surface (73), (
75) and the second curved surfaces (74) and (76) are in contact with each other, the balance can be easily maintained unlike the Oldham joint, and high-speed rotation can be performed. Furthermore, since only the engaging members (71) and (72) are provided, the number of parts is small and a plurality of engaging members (71) are provided.

(72) are in contact with each other in order, so that wear can be reduced.

In addition, since the engaging members (71) and (72) are in contact with each other at the curved surfaces (73) to (76) on the normal rotation side and the reverse rotation side, the relative angles of both scrolls (3) and (4) can be adjusted accurately. It is possible to keep the wrap (32), (4
2) Abnormal contact can be reliably prevented.

Furthermore, energy can be exchanged between the curved surfaces (73) and (76) and the fluid, and for example, a supplementary effect can be exerted.

Further, according to the invention according to claim (5), since the fluid flows along the flow path (78), the flow rate of the fluid can be reliably maintained, and energy can be transferred and received efficiently. can be improved.

Further, according to the invention according to claim (6), the thrust force of both scrolls (3) and (4) is transferred to one thrust bearing (8).
), the thrust force can be reliably stopped and mechanical loss can be significantly 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. Furthermore, the driving side frame (5) is fixed to the casing (2) at the flange (5a) formed on the outer peripheral edge, and the driven side frame (6) is fixed to the outer peripheral surface of the casing (2). And both frames, Z, (5),
In the center of (6) are each of the above scrolls (3), (
Shaft holes (51) and (61) for rotatably supporting the shafts (51) and (61) are bored in the vertical direction, and both shaft holes (51) and (6
1) is formed so that the axes are spaced apart from each other by a predetermined distance in the radial direction.

Both scrolls (3) and (4) have disk-shaped end plates (31) and (41), and involute shaped knobs (32) and (42) formed on the front surface of the disk-shaped end plates (31) and (41).
are constructed by standing upright, and both mirror plates (31), (41
) with their front faces facing each other, both of the frames (5),
(6) Each of the above wraps (32) is arranged in parallel between the
, (42) are intermeshed with each other. Further, a drive shaft (33) is provided on 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).
A driven shaft (43) is connected to the back surface (upper surface) of each frame (4), and the drive shaft (33) and driven shaft (43) are connected to the shaft hole (51) ( 6
1) via radial bearings (34) and (44) so as to be rotatable. In addition, each of the above mirror plates (31),
(41) and each frame (5).

(6) and the thrust bearing (35), (45)
are interposed, and the scrolls (3) and (4) are supported by the frames (5) and (6). The drive shaft (33) extends to the bottom of the casing (2) and is fitted into the rotor (12a) of the drive motor (12). Furthermore, the stator (12b) of the drive motor (12) is attached to a support member (52) connected to the lower part of the drive side frame (5), and a stator (12b) is formed at the lower end of the support member (52). Inward flange (52a)
The lower part of the drive shaft (33) is fitted into and supported by the lower part of the drive shaft (33).

Further, the drive shaft (33) and the driven shaft (43) are provided so that the drive 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 (7), and one scroll (3) or (4) is relatively connected to the other scroll (4) or (3). ) 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 working chamber. (13), and the action chamber (13) is configured to contract while moving toward the center of both scrolls (3) and (4).

Inside the casing (2), the lower part of the frame (5) is made into a low pressure chamber (21) by the driving side frame (5), and the upper part of the frame (6) is made into a high pressure chamber (22) by the driven side frame (6). A wrap (32) between both frames (5), (6),
(42) is formed in the suction chamber (23). On the side of the casing (2) is a low pressure chamber (2).
A suction pipe (24) is connected to the upper part of the high pressure chamber (22).
The discharge pipes (25) are connected to each other.

In addition, the flange (5) on the drive side frame (5)
A communication passage (53) is bored at the base of the frame (5) over both the upper and lower sides of the frame (5), and the low pressure chamber (21) and the suction chamber (22) are communicated with each other through the passage (53). The low pressure refrigerant gas is configured to flow into the sealed chamber (13) from the suction chamber (23). Furthermore, the above-mentioned driven scroll (4)
A discharge passage (46) is bored in the center of the head plate (41) from the front face of the driven shaft (43) to the end face (upper face) of the driven shaft (43), and high pressure refrigerant gas is supplied from the action chamber (13) to the high pressure chamber (22). ). Furthermore, the bottom of the casing (2) is an oil reservoir (26) for lubricating oil, and the oil reservoir (26) has an oil supply pump (36) installed at the lower end of the drive shaft (33). ) is soaked in water, and lubricating oil is supplied to each bearing (34), (35), etc. from the oil supply pump (36) through an oil supply path (not shown).

On the other hand, the above-mentioned connecting means (7), which is a feature of the present invention,
As shown in FIG. 3 and FIG. 3, a plurality of drive pins (71), (71), . A plurality of driven pins (72), (72), which are driven side engagement members on the outer peripheral edge of the end plate (41) in (4),
... are formed and configured respectively. Both pins (
71) and (72) are provided at equal intervals of eight each, and are erected from the front of one tAk (31) and (41) toward the other mirror plate (41) and (31) facing each other, Both pins (71) and (72) are configured to contact and engage with each other.

Furthermore, the side surface of the drive pin (71) in the normal rotation direction (see FIG. 2A) is the first curved surface (73), and the side surface in the reverse direction (second direction) is the first curved surface (73).
The side surface of the driven pin (72) in the reverse direction (see FIG. 2B) is formed as a second curved surface (74), while the side surface of the driven pin (72) in the reverse direction (see FIG. 2B) is formed on the first curved surface (75) in the forward direction ( Figure 2A
) is formed on the second curved surface (, 76).

And between each of the driving pins (71), (71), . . ., each driven pin (72), (72), .
Conversely, each drive pin (71), (71), ... is located between each driven pin (72), (72), ..., respectively, and both pins (71), (72) The first curved surfaces (73) and (75) of each other and the second curved surface (74)
.

(76) are formed to face each other and to be able to contact each other.

Also, both turning surfaces (73) (74) of the drive pin (71)
is formed in a concave shape curving toward the centrifugal direction of the end plate (31) in plan view, and is formed by an arc of a large diameter opening C1 with a predetermined radius, while both turning surfaces (75) of the driven pin (72) ), (76) is the mirror plate (41) in plan view.
It is formed in a convex shape that curves toward the centrifugal direction of the
The large diameter opening C1 and the radius circle C are formed into a closed curve having each curved surface (73) to (76) as a part. The large-diameter opening C1 forms an envelope of a radius circle C:, which means that as the scrolls (3) and (4) rotate, the pins (71) and (72) move in the circumferential direction. Each of the curved surfaces (73) to (76) is formed so that the corresponding large-diameter opening C1 always touches the radius circle at one point.

Furthermore, the first curved surface (73) of both the pins (71) and (72)
), (75) are formed so as to be in contact with each other within a predetermined rotation range Dl during one rotation of both the pins (71) and (72), and within this rotation range, the drive scroll (3) The rotating force is transmitted to the driven scroll (4) via both pins (71) and (72).

On the other hand, the two curved surfaces (74) of the above-mentioned pins (71) and (72)
, (76) are formed so as to come into contact with each other within a predetermined rotation range located approximately symmetrically to the rotation range D1 during one quarter rotation of both the pins (71) and (72),
First curved surface (73).

The relative angle between the scrolls (3) and (4) is maintained by the contact between the scrolls (75) and the second curved surfaces (74) and (76).

Furthermore, each curved surface (73) in the drive pin (71),
(74) is formed so that the arc center El, that is, the center E1 of the large diameter opening C1, is located on a concentric circle centered on the drive shaft center 01, and each curved surface (75), ( 76) is the arc center E, that is, the radius circle C
The center E of 2 is located on a concentric circle centered on the driven axis O:. And the above driven pin (
The radius of curvature r of each curved surface (75) and (76) in (72), that is, the radius r of the radius circle is the same as the driven pin (72).
) (eight in this example) and the center distance R between the driven axis 02 and the center E of the radius circle. On the other hand, each curved surface (73) in the drive pin (71),
The radius of curvature "1" in (74), that is, the radius "1" of the large diameter opening C1, is the eccentricity between the drive shaft center OI and the driven shaft center 〇2.
Then, as shown in the following equation, r2-r) +R(1-CD is set, and specifically, the radius of curvature r is set slightly larger than the equation (2).

Further, the arc angle θ1 of each of the curved surfaces (73) to (76) is also included.
θ: is set to θ1-θko-(2π)/N...■, as shown in the following equation, assuming the number of pins (71) and (72) is N (8 in this example). Specifically, the arc center θ1. θ is set slightly larger than the 0 formula.

Therefore, the specific shapes of each of the curved surfaces (73) to (76) are shown in Table 1, for example.

Table 1 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. So, drive pin (71).

(71), . . . also rotate around the drive shaft center (01). Any one of the drive pins (71,), (71), . . . , for example, in FIG. 2, the three drive pins (71), (71), . The first curved surface (73) is the driven pin (72) (72),...
The rotational force of the driving scroll (3) or the driven pin (72) is tangent to the first curved surface (75) of [7.

(72), . . . are transmitted to the driven scroll (4). Due to this power transmission, the driven scroll (4) rotates around the driven axis (0:), and furthermore, the driven scroll (4) rotates in synchronization with the driving scroll (3),
According to this synchronous rotation, one scroll (3) or (4)
), the other scroll (4) or (3) only revolves relative to it. Along with this revolution, there is a wrap (
32) and (42) toward the center, and the action chamber (13) moves between the wraps (32) and (42).
) are formed from the outer peripheral ends of the wraps (32) and (42), and the action chamber (13) contracts while moving in a spiral shape toward the central discharge passage (46).

On the other hand, low-pressure refrigerant gas is supplied from the suction pipe (24) to the casing (
2) flows into the low pressure chamber (22) in the interior and passes through the suction chamber to the curved surfaces (73) at each of the pins (71) and (72).
It flows into the action chamber (13) through the gap (76). Then, due to the contraction of the action chamber (13), the low-pressure refrigerant gas is compressed into high-pressure refrigerant gas! Therefore, the high-pressure refrigerant gas passes through the discharge passageway (46), flows into the high-pressure chamber (22), and is then discharged from the discharge pipe (25).

In addition, the second curved surface (
74) and (76) are in contact within a predetermined rotation range, and the relative angle of both scrolls (3) and (4) is maintained by the contact between the first curved surfaces (73) and (76), and the driving scroll When the scroll (3) decelerates, the driven scroll (4) also decelerates in accordance with the drive scroll (3).

Therefore, a plurality of drive pins (71), (71).

... and driven pins (72), (72), ... are provided on both scrolls (3), (4), and the first curved surface (7
3).

Since (75) and the second curved surfaces (74) and (76) are in contact with each other, balance can be easily maintained unlike the Oldham joint, and high-speed rotation can be performed. Furthermore, both the above pins (71), (7
2), the number of parts is small, and a plurality of pins (71,) are provided.

(72) are in contact with each other in order, so that wear can be reduced.

In addition, since each of the above pins (71) and (72) touch at six tracks 1f1j (73) to (76) on the forward and reverse rotation sides, the relative angles of both scrolls (3) and (4) can be adjusted accurately. Wrap when stopping, etc. (32),
The abnormal contact (42) can be reliably prevented.

Furthermore, energy can be transferred between each of the curved surfaces (73) and (76) and the fluid, and a supplementary effect can be exerted.

FIG. 4 shows another embodiment with a curved surface shape, in which the drive pin (71, a) and the driven pin (72a) are formed to have the same shape in plan view.

In other words, the first curved surface (73a) of the drive pin (71a)
and the second curved surface (76a) of the driven pin (72a) are formed in a concave shape in plan view, and are formed in an arc having a large diameter circle C1. On the other hand, the second curved surface (7) of the drive pin (71a)
4a) and the first curved surface (75a) of the driven pin (72a) are formed in a convex shape in plan view, and are formed in an arc having a small diameter circle C2. Then, each of the curved surfaces (73a) to (76a
), the radius of curvature rl+'2, that is, the radius r of the large diameter circle C1
1 and small diameter circle C! The radius r2 of the previous example (see Figure 2)
The curved surfaces (73a) to (73a) to (73a) facing each other are set similarly to
6a) has a concave shape and a convex shape. One surface of this plan (
73a) and (75a), the rotational force of both scrolls (3) and (4) is transmitted, and the
Curved surface (73a).

(75a) and the second curved surface (74a), (76a
), the relative angle between both scrolls (3) and (4) is maintained.

Other configurations, functions, and effects are the same as in the previous embodiment.

FIG. 5 shows another embodiment of the engagement member, in which the drive piece (71b) which is the drive side engagement member is attached to the drive scroll (3).
It is formed on the same plane as the mirror plate (31).

In other words, the end plate (31
) is formed with a plurality of substantially U-shaped notches (3a), and each of the notches (3a).

A drive piece (71b) is formed between (3a), . The drive piece (7], b) has a concave first curved surface (73b) on the side surface in the normal rotation direction, similar to the drive pin (71) in the previous embodiment (FIGS. 2 and 3). , the side surface in the direction of the reverse force is formed into a concave second curved surface (74b).

On the other hand, the driven pin (7) provided on the driven scroll (4)
2b) is the driven pin (7) of the previous embodiment (Figs. 2 and 3).
2), the first curved surface (75b) and the second curved surface (76b
) is formed, and the end plate (
31), and is configured to engage with the drive piece (7), b).

Other configurations, functions, and effects are the same as in the previous embodiment.

In this embodiment, the driven pin (72b) is formed long, but the driving pin (71) shown in FIG. 2 is formed long, and the driven side engagement member is formed on the outer peripheral edge of the mirror plate (41). You may.

Further, each of the curved surfaces (73b) to (76b) may have the shape shown in FIG.

FIGS. 6 and 7 show another embodiment in which each engaging member is formed from a separate member. In the drawings, only the drive-side engaging member is shown.

The drive-side engaging member shown in FIG. 6 is a drive pin (71) formed in the same shape as the drive pin (71) of the previous embodiment shown in FIG.
c). And the drive pin (71c)
are formed on the upper surface of the ring member (77), and each drive pin (71, c), (71
c), . . . are integrally formed, and the ring member (77) and drive pins (71c), (71C), . . . are formed separately from the drive scroll (3). Further, the ring member (77) is formed of a flat plate material, and its outer peripheral end is formed to match the outer peripheral end of the end plate (31) of the drive scroll (3), and its inner peripheral end is formed to match the outer peripheral end of the end plate (31) of the drive scroll (3). It is formed to have a larger diameter than the end of the winding.

On the other hand, a positioning pin (14) and a bolt (15) are provided between the ring member (77) and the end plate (31), and the ring member (77) has a positioning hole (14a).
) and a mounting hole (15a) for the bolt (15), and the end plate (31) has a positioning hole (14b) and a screw hole (
15b) are drilled.

Next, this drive scroll (3) and drive pin (71c
) formation and installation will be explained below.

First, the drive scroll (3) is formed separately and independently, while the drive pins (71c), (71c).

... and the ring member (77) are formed separately.

Then, a ring member (77) is placed on the front surface of the end plate (31) of the drive scroll (3), and the positioning pin (14) is inserted into both positioning holes (14a) and (14b).
Insert the bolt (15) into the screw hole (1) through the mounting hole (15a).
5b), and the ring member (77) and drive pin (7
1c), (71C),... are driven by the scroll (3
) to complete the assembly.

Therefore, the drive scroll (3) and drive pin (71c)
), (71c), ... are formed separately, so
Molding can be facilitated. Furthermore, the distance between the drive pin (71c) and the winding end of the wrap (32) can be set small, and the entire drive scroll (3) can be made compact.

Other structures, functions, and effects are the same as those of the previous embodiment shown in FIGS. 1 to 3.

Note that the driven pin is not shown or the driving pin (
71c) may be formed through a ring member, or as shown in FIG.
c) may be made longer and a driven piece may be formed on the outer peripheral edge of the end plate (41).

Further, the shape of the drive pin (71c) may be as shown in FIG. 4.

The ring member (77a) shown in FIG. 7 is formed thickly,
The height in the vertical direction is higher than that of the ring member (77) shown in FIG. As shown in FIG. 8, a plurality of refrigerant gas flow passages (78) are formed in the ring member (77a). The flow passage (78) is formed in an inverted U-shape in cross section and opens at the lower surface of the ring member (77a), and extends from the outer peripheral surface to the inner peripheral surface of the ring member (77a). Furthermore, the flow passage (78) is formed in a spiral shape that winds in a direction opposite to the normal rotation direction A of the drive scroll (3). Then, place the positioning pin (14
) etc. are the same as in the embodiment shown in FIG.

Therefore, when the drive scroll (3) is rotated, the refrigerant gas passes from the suction chamber (23) through the flow path (78) and wraps (
32) and (42) into the action chamber (13). This flow path (78) makes it possible to ensure a sufficient flow rate of the refrigerant gas, and also to give centripetal force to the refrigerant gas, improving suction efficiency, thereby improving volumetric efficiency during high-speed rotation. be able to.

Other structures, functions and effects are the same as those of the embodiment shown in FIG.

Figures 9 and 10 show another embodiment of the thrust member (8), including both scrolls (3).

The thrust force (4) is stopped by one thrust bearing (8).

In other words, the thrust bearing (8) is connected to the driven scroll (4).
The thrust member (8) is formed as a flat ring member.

On the other hand, the four drive pins (
71), (71), ... are formed with protrusions (81), which are provided at equal intervals, and whose upper surfaces almost coincide with the back surface of the end plate (41) of the driven scroll (4). It is formed to do so. Further, the end plate (41) of the driven scroll (4) has four notches (82) formed at its outer periphery, through which the projections (81) pass.

Then, the thrust bearing (8) is connected to the protrusion (81) (81).
), . . by bolts (83), (83), . . . and fixed to the drive scroll (3).

In addition, in this example, the thrust bearing (3
5) and (45) are not provided.

Therefore, when refrigerant gas is compressed between both scrolls (3) and (4), a thrust force is applied to both scrolls (3) and (4) to separate them from each other, and the driving scroll (3)
) is pushed downward, and the driven scroll (4) is pushed upward. The thrust force is then stopped by a thrust bearing (8). In other words, both the above scrolls (3), (4)
The thrust forces acting in opposite directions are canceled out by one thrust bearing (8).

As a result, the thrust bearing (8) can stop receiving the thrust force, and at the same time, the thrust bearing (8) can stop receiving the thrust force.
) is fixed to the driving scroll (3), so it performs only revolution movement relative to the driven scroll (4), and mechanical loss can be significantly reduced.

In addition, since the thrust bearing (8) is fixed using the drive pin (71), the fixing members etc. are both scrolls (3),
(4) There is no outward protrusion, and the entire device can be made smaller.

Other structures, functions, and effects are the same as those of the previous embodiment shown in FIGS. 1 to 3.

In this embodiment, the thrust bearing (8) is fixed to the drive scroll (3), but it may also be fixed to the driven scroll (4) and provided on the back side of the end plate (31) of the drive scroll (3).

In addition, a driving pin (71) or a driven pin (72) is integrally molded on the thrust bearing (8), and each pin (71), (72) is integrally formed with the thrust bearing (8).
) may be attached to the mirror plates (31) and (41). At that time, one of the engaging members is the drive piece (7) shown in FIG.
As shown in 1b), they are formed on the outer periphery of the mirror plates (31) and (41).

Further, the pins (71) and (72) may be those shown in FIG.

Furthermore, although each embodiment has been described with respect to a compressor, the present invention may be used in a blower, an expander, or the like.

[Brief explanation of drawings]

1 to 10 show embodiments of the present invention.
The figure is a longitudinal cross-sectional view of the scroll type fluid device, FIG. 2 is a cross-sectional end view taken along the line U-U in FIG. 1, and FIG. 3 is a perspective view of the scroll mechanism. Figure 4 is a view equivalent to Figure 2 showing another curved surface, Figure 5 is a view equivalent to Figure 3 showing a drive piece, Figure 6 is an exploded perspective view showing another drive pin, and Figure 7 is another ring. A view corresponding to FIG. 6 showing the member, and FIG. 8 are a plan view of the ring member. FIG. 9 is a longitudinal sectional view of a scroll type fluid device showing another embodiment of the thrust bearing, and FIG. 10 is an exploded perspective view of the scroll mechanism. (1)... Scroll type fluid device (2)... Sealed casing (3)... Drive scroll (4)... Followed scroll (7)... Connection means (8)... Thrust bearing (31), (41)... End plate (32), (42)... Wrap (33)... Drive shaft (43)... Driven shaft (71), (71a), (71b), (71c) (72
a) (73a) (74a) (75a), (76a), (77a)...Flow path...Drive pin (72). (73). (74) (75) (76) (77) (78) (72b), (73b) (74b), (75b), (76b)...Ring member...Driver pin...First curved surface... ...2nd curved surface...1st curved surface...2nd curved surface and 2 other people Figure 3 (1+ Scroll semiconductor device (2) Captured canon (3), g7 moving scroll (4) Driven scroll (7) )・J!Kichoudan (8) Thrust Tsumugi 2 (31), (4])・-Kagamiita (32+, (42)-Rap (33) Edict #9 (43) Followed Yuu (71), ( 71a1. (71b), (7]e) Pivot pin (72) (73) (74) <75> (76) (17) (7R) (72b) - Follower pin (73b) First opening (74b)・2nd curved surface <75b) 1st) 111th surface (76b) ・2111111i+ ・・Rishiku part I (72a) (73a) (74a) (75a) (76ml (77 pieces) Sei 7! I28 b Fig. 1 Figure 5 Figure 36 Figure 9 Figure 10

Claims (1)

[Scope of Claims] (1) A drive scroll (3) comprising a spiral wrap (32) erected on the front side of the end plate (31) and a drive shaft (33) connected to the back side; ) and a driven scroll (4) having a spiral wrap (42) erected on the front surface and a driven shaft (43) connected to the back surface of each wrap (3).
2) and (42) are disposed in parallel in mesh with each other, the scrolls being arranged so that the driven scroll (4) rotates synchronously with the rotation of the driving scroll (3). (3
), (4), and the connecting means (7) includes a plurality of drive-side engagements formed on the outer periphery of each of the end plates (31), (41) and engaging with each other. Consisting of mating members (71), (71), ... and driven-side engaging members (72), (72), ..., each scroll in both the engaging members (71), (72) The side surfaces of (3) and (4) in the forward and reverse rotation directions are curved in the centrifugal direction of the end plates (31) and (41), and can slide into contact with each other between the engaging members (71) and (72). The first time to face
Curved surfaces (73), (75) and second curved surfaces (74), (76
), while the first curved surfaces (73), (75) and the second curved surface (74),
(76) is one of the first and second curved surfaces (75) and (76
) on the envelope of the closed curve that is a part of the other first and second
A scroll-type fluid device characterized in that it is formed so that curved surfaces (73) and (74) are positioned. (2) In the scroll type fluid device according to claim (1), the first curved surface (73), (75) and the second curved surface (74)
, (76), one of the first and second curved surfaces (75), (
76) is formed by a circular arc with a predetermined radius of curvature r_2, and the other first and second curved surfaces (73) and (74) are formed by the drive shaft (
33) and the driven shaft (43) is R_0, and the scroll type fluid device is formed by a circular arc with a radius of curvature r_1 approximately equal to r_1=r_2+R_0. (3) In the scroll type fluid device according to claim (1) or (2), both engaging members (71a) and (71b) are
A scroll-type fluid device characterized by being formed to have the same shape in plan view. (4) In the scroll type fluid device according to claim (1), (2) or (3), one of the engaging members (72b) is provided upright on the outer peripheral edge of the end plate (41) and faces the end plate (41). 31
), and the other engaging member (71b) is formed on the outer peripheral edge of the end plate (31). (5) In the scroll type fluid device according to any one of claims (1) to (4), a ring member (77a) is provided on the front outer peripheral edge of at least one end plate (31).
is formed to protrude toward the opposing end plate (41), and the ring member (77a) has one engagement member (71c).
A scroll-type fluid device characterized in that a flow path (78) through which fluid passes is formed in a spiral shape from an outer circumferential surface to an inner circumferential surface. (6) In the scroll type fluid device according to any one of claims (1) to (5), a thrust bearing (8) is provided in contact with the back side of one end plate (41), and the thrust bearing (8) A scroll type fluid device characterized in that the bearing (8) is fixed to an engaging member (71) provided on the other end plate (31).