JPH0610601A - Scroll type fluid device - Google Patents

Abstract

PURPOSE:To revolve a two-teeth type revolution scroll arranged between a pair of fixed scrolls in the mechanism of a simple construction such as the angle maintaining mechanism of a crank mechanism and an Oldham's mechanism which are used in a conventional type of a single tooth type, and also eliminate an up-setting moment which acts on the revolution scroll by means of a simple structure. CONSTITUTION:A revolution scroll 6 is maintained on a revolution axial body 7 having first and second engaging parts 7a, 7b which are positioned on back surface sides of respective fixed scrolls 4, the first engaging part 7a is engaged with a rotary driving shaft 11 through a crank mechanism 10, the second engaging part 7b is maintained revolvably on an eccentric bearing 9, and an angle maintaining mechanism 18 is provided.

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 used as a rotary compressor or the like.

[0002]

2. Description of the Related Art Conventionally, a scroll type fluid device having a revolving scroll of a so-called single tooth type in which a spiral wrap is erected only on one surface of an end plate is well known. But,
In this type of scroll type fluid device, when the fluid taken in the working chamber formed between the orbiting scroll and the fixed scroll is compressed by contraction of the working chamber, the orbiting scroll is thrust by the reaction force at the time of compression. However, there is a problem in that a loss due to a thrust load is likely to occur due to the large load.

Therefore, in recent years, a scroll-type fluid device equipped with a so-called double-tooth type revolving scroll has been attracting attention in order to achieve a perfect balance of thrust load. As an example of such a scroll type fluid device, Japanese Patent Application Laid-Open No. Sho 61-61 is known.
There is one known in Japanese Patent Publication No. 58991. In this conventional example, as shown in FIG. 10, a pair of fixed scrolls (a) and (a) are arranged so that the wrap (b) sides face each other, and between the fixed scrolls (a) and (a). The orbiting scroll (A) in which the wraps (d) are respectively erected on both sides of the end plate (c) is arranged. Then, since the working chambers (e) and (e) are formed on both sides of the end plate (c) of the orbiting scroll (A), a small radial load (R) due to the reaction force at the time of fluid compression still remains, Large loads (T) in the thrust direction can be canceled by each other, and the thrust loads (T) acting on the orbiting scroll (A) can be balanced.

In this conventional example, in order to revolve the orbiting scroll (A) with a relatively simple structure, both fixed scrolls (a), (a) are moved from the position near the end of the rotary drive shaft (f). An auxiliary member (B) that extends beyond one fixed scroll (a) is used for the orbiting scroll (A), and the orbiting scroll (A) is held by this auxiliary member (B). With this structure, a simple crank mechanism having a structure used for a single-tooth type can be interposed between the auxiliary member (B) and the rotary drive shaft (f) substantially as it is, and the auxiliary member (B) can be used. An angle maintaining mechanism with a simple structure such as the Oldham mechanism is fixed on both scrolls (a), (a).
It can be installed without interfering with.

[0005]

However, in the above-mentioned conventional example, the revolving scroll (A) is supported only on the side of the rotary drive shaft (f) through the auxiliary member (B), so to speak, cantilever support. Therefore, in the orbiting scroll (A), it is inevitable that the radial load (R) causes a rollover moment (M) around the engaging portion with the rotary drive shaft (f). As a result, scroll (a),
Problems such as the laps (b) and (d) twisting together between (A) occur.

In the case of the single tooth type, as shown in phantom in FIG. 10, a thrust bearing (k) is provided at a position on the back side of the auxiliary member (B), and the orbiting scroll (k) is provided on the thrust bearing (k). The thrust load (T) can be used for pressing so that A) is not overturned. However,
In the case of the double-tooth type, the thrust bearing (k) cannot sufficiently cope with the overturning moment (M) as long as the thrust load (T) is balanced. Therefore, it cannot be put to practical use as it is, and it is actually difficult to achieve a perfect balance of the thrust load with such a simple structure.

In the above description, the case where the two-tooth type revolving scroll (A) is arranged between the pair of fixed scrolls (a) and (a) has been described. The situation is the same even when the fixed scroll is arranged between a pair of one-tooth type revolving scrolls.

An object of the present invention is to eliminate the overturning moment acting on the orbiting scroll with a simple structure in a scroll type fluid device equipped with a double-tooth type scroll, and to revolve the orbiting scroll with a relatively simple structure. Is to let.

[0009]

To achieve the above object, in the present invention, the revolution scroll is supported not only on the side of the rotary drive shaft but also on the opposite side along the axis.

Specifically, in the invention of claim 1, as shown in FIGS. 1 and 2, a pair of fixed scrolls (4) each having a wrap (4b) standing on one side of an end plate (4a). ，
Between (4), wrap (6b) on both sides of the end plate (6a),
The scroll mechanism section (2) is configured by disposing the orbiting scrolls (6) in which (6b) are respectively erected, and restricts the rotation of the orbiting scroll (6) according to the drive of the rotary drive shaft (11). It is premised on a scroll type fluid device which is revolved around the axis (P).

Then, the revolution assisting body (7) having the first and second engaging portions (7a), (7b) located on the back side of the end plate (4a) of each fixed scroll (4) is The orbiting scroll (6) is provided by the orbiting auxiliary body (7) so as to be able to orbit the fixed scrolls (4) and (4).
Hold. The first engaging portion (7a) is engaged with the rotary drive shaft (11) via the crank mechanism (10), while the second engaging portion (7b) is revolved into the eccentric bearing (9). Hold as much as possible. Further, an angle maintaining mechanism (18) is provided that enables the revolution assisting body (7) to revolve while restricting its rotation.

According to the second aspect of the invention, as shown in FIG.
Between the pair of orbiting scrolls (6) and (6) in which the wrap (6b) is erected on one side of the end plate (6a), the end plate (4
A scroll mechanism portion (2) is configured by disposing fixed scrolls (4) in which wraps (4b) and (4b) are respectively erected on both sides of a), and depending on the drive of the rotary drive shaft (11). The premise is a scroll type fluid device in which both orbiting scrolls (6) and (6) are revolved around an axis (P) while restricting rotation.

Then, the revolution assisting body (7) having the first and second engaging portions (7a) and (7b) located on the back side of the end plate (6a) of each of the orbiting scrolls (6) is fixed. The revolving auxiliary body (7) holds the two orbiting scrolls (6) and (6) so that they can revolve around the scroll (4). The first engaging portion (7a) is engaged with the rotary drive shaft (11) via the crank mechanism (10), while the second engaging portion (7b) is revolved into the eccentric bearing (9). Hold as much as possible. Further, an angle maintaining mechanism (18) is provided that enables the revolution assisting body (7) to revolve while restricting its rotation.

According to a third aspect of the present invention, in the above-mentioned first aspect of the present invention, the internal space of the casing (1) for accommodating the scroll mechanism section (2) is a space for disposing the scroll mechanism section (2). The space (23) and the high-pressure space (22), which is a discharge space of the high-pressure fluid compressed by the scroll mechanism portion (2), are partitioned by a partition wall (5b), and the partition wall (5b) forms a second engagement portion. When (7b) is rotatably held, the end plate (4) of the fixed scroll (4) on the same side as the second engaging portion (7b) of the revolution assisting body (7).
a) A discharge hole (4c) is provided in the center of the end plate (4a) for communicating the spaces on both sides of the end plate (4a) with each other, and a discharge hole (4c) for communicating the discharge hole (4c) with the high pressure space (22) is provided in the engaging portion (7b). (7
d) is provided. Also, the revolution assisting body (7) and the end plate (4)
An annular seal member (24) slidably contacting at least one of the two is provided between the lead hole (7d) and the discharge hole (4).
It is provided so as to surround the opposite open ends of c).

According to a fourth aspect of the invention, the first or second aspect of the invention is provided.
In the invention of FIG. 5, as shown in FIG.
The revolving auxiliary body (7) and the revolving scroll (6) are attached to the first engaging portion (7a) side end portion of 1) and the eccentric bearing (9).
Balancers (11b) and (9a) are provided for canceling the eccentric moment generated by the orbital movement of the.

According to the invention of claim 5, in the invention of claim 4, as shown in FIG. 6, the center of gravity (G1) of the balancer (11b) of the rotary drive shaft (11) is located on the revolution assisting body (7) side. It is set at a position retracted in the rotational direction by a predetermined phase angle (θ1) from the position having a phase difference of 180 ° with respect to the center of gravity (G). On the other hand, as shown in FIG. 7, the center of gravity (G2) of the balancer (9a) of the eccentric bearing (9) is set to a position more than the position having a phase of 180 ° with respect to the center of gravity (G) of the revolution assisting body (7). The phase angle (θ2) is set to a position advanced in the rotation direction.

[0017]

In the invention of claim 1 or 2, since the first engaging portion (7a) of the revolution assisting body (7) is engaged with the rotary drive shaft (11), the revolution scroll is the same as the conventional one. (6) can be supported on the side of the rotary drive shaft (11). And the 2nd engaging part (7b) of the revolution auxiliary body (7)
Is retained by the eccentric bearing (9) so that it can revolve,
The orbiting scroll (6) can also be supported on the opposite side of the rotary drive shaft (11) along the axis (P). Thus, the revolution assisting body (7) having the first and second engaging portions (7a) and (7b) located on the side of the rotary drive shaft (11) of the scroll mechanism portion (2) and on the opposite side thereof, respectively. Using
By holding the revolution scroll (6) on it,
The orbiting scroll (6) can be supported on both sides of the rotation drive shaft (11) and the opposite side along the axis (P). Therefore, it is possible to support the orbiting scroll (6) against the radial load (R) so that it can revolve without overturning.

Moreover, by utilizing the fact that the first engaging portion (7a) of the revolution assisting body (7) is on the side of the rotary drive shaft (11), the structure used for the one-tooth type The simple crank mechanism (10) can be interposed between the first engaging portion (7a) and the rotary drive shaft (11) substantially without any interference with the fixed scroll (4). Further, a simple angle maintaining mechanism (18) having a structure such as an Oldham mechanism used for a one-tooth type can be attached to the revolution assisting body (7) substantially without any interference with the fixed scroll (4). Therefore, the orbiting scroll has a relatively simple structure (6)
Can be revolved around.

In the invention of claim 3, the internal space of the casing (1) for accommodating the scroll mechanism portion (2) according to the invention of claim 2 is a space for disposing the scroll mechanism portion (2). Space (23) and scroll mechanism (2)
High pressure space (2 which is the discharge space of the high pressure fluid compressed by
2) and the partition wall (5b).
When the second engaging portion (7b) is rotatably held by b), the lead-out hole (7d) is provided in the second engaging portion (7b) of the revolution assisting body (7), and the lead-out hole (7d) is provided. Hole (7d)
Thus, the discharge hole (4c) provided in the central portion of the end plate (4a) of the fixed scroll (4) is communicated with the high pressure space (22). As a result, the discharge passage for the compressed fluid is connected to the low pressure space (2
3) can be formed. Furthermore, since the annular sealing material (24) interposed between the revolution assisting body (7) and the end plate (4a) surrounds the lead-out hole (7d) and the discharge hole (4c) facing each other. The discharge passage can be partitioned from the low pressure space (23). Incidentally, the sealing material (24)
Since it can be slidably contacted with at least one of the revolution assisting body (7) and the end plate (4a), no problem occurs in the revolution of the revolution assisting body (7).

This is because the revolving auxiliary body (7) has the second engaging portion (7b) at the rear side position of the fixed scroll (4) opposite to the rotary drive shaft (11). In some cases the fixed scroll (4) provides a high pressure space (2
2) and the low pressure space (23) are partitioned to form a high pressure space on the back side of the fixed scroll (4), that is,
The low pressure space (23) is also the space on the back side of the fixed scroll (4).
Therefore, since the high pressure fluid cannot be discharged as it is from the discharge hole (4c) provided in the fixed scroll (4) to the back side space, the discharge passage of the high pressure fluid is provided in the low pressure space (23). It is a means for solving the problem of newly securing, and at that time, a part of the revolution assisting body (7), the second engaging portion (7b), and the eccentric bearing (9) which are arranged in the back side space. It is also a solution to the problem of avoiding interference.

In the invention of claim 4, the rotary drive shaft (11)
By providing the eccentric bearing (9) with balancers (11b) and (9a) for canceling the unbalance caused by the revolution movement of the revolution auxiliary body (7) and the revolution scroll (6), respectively. Axial center of (7) (P)
The above imbalance is offset well in both directions.

This is because, in the invention of claim 1 or 2, when the imbalance caused by the revolution movement of the revolution scroll (6) and the revolution assisting body (7) is eliminated, the rotary drive shaft (11 It is to solve the problem that the dynamic balance is basically poor if the balance weight is only provided on the () side. In particular, considering that the unbalance itself is large due to the addition of the revolution assisting body (7), weighting the balance weight on the rotary drive shaft (11) side causes the above-mentioned imbalance in dynamic balance. There is a risk that it will become apparent, and there is also a risk that the air resistance of the balancer will increase as the weight increases, and the loss of the device will increase.

In the invention of claim 5, the rotary drive shaft (11)
The balancer (11b) has a center of gravity (G1) at a rear side in the rotation direction by a predetermined phase angle (θ1) from a position having a phase difference of 180 ° with respect to the center of gravity (G) of the revolution auxiliary body (7). Therefore, the center of gravity (G1) is positioned at an appropriate position having a phase difference of 180 ° with respect to the center of gravity (G) on the side of the revolution assisting body (7) during revolution. On the other hand, the center of gravity (G) of the balancer (9a) of the eccentric bearing (9)
Also for 2), this center of gravity (G2) is the revolution auxiliary body (7).
The center of gravity (G2) is located at the front side in the rotation direction by a predetermined phase angle (θ2) with respect to the position having a phase difference of 180 ° with respect to the center of gravity (G) on the side, so that the center of gravity (G2) is revolved during revolution. ) Side center of gravity (G), it will be positioned at an appropriate position having a phase difference of 180 °.

This is because there is a phase difference between the rotational movement of the rotary drive shaft (11) and the orbital movement of the orbiting scroll (6) due to the presence of a clearance or the like in the bearing portion, and the rotary drive shaft on the drive side. When the revolution of the revolution assisting body (7), which is the driven side with respect to (11), is delayed by a predetermined angle in the rotational direction, the center of gravity (G1) of the balancer (11b) is moved toward the revolution assisting body (7) side. This is to solve the problem that the accuracy of the balance actually decreases when the position is set to have a phase difference of 180 ° with respect to the center of gravity (G). This is the same between the revolution assisting body (7) and the eccentric bearing (9).

[0025]

Embodiments of the present invention will now be described in detail with reference to the drawings.

(Embodiment 1) In Embodiment 1, the scroll type fluid device is used as a compressor for a refrigerator and compresses and discharges a refrigerant gas. The scroll compressor according to this embodiment has a hermetic casing (1) as shown in FIG. 2, and a scroll mechanism portion (2) for sucking and compressing and discharging a refrigerant gas is provided above the inside of the casing. ) Is housed therein, and has a drive mechanism section (3) having a motor (16) for driving the scroll mechanism section (2) below.
Is housed. A suction pipe (1a) for sucking the refrigerant gas is provided on an upper portion of a side wall of the casing (1) so as to project laterally, and an upper end wall of the casing (1) for discharging the compressed refrigerant gas. A discharge pipe (1b) is provided so as to project upward.

The scroll mechanism section (2) comprises a pair of upper and lower fixed scrolls (4) and (4), and each fixed scroll (4) is fixed to the inner wall surface of the casing (1) (5). ) Is supported and fixed by.
Each of the fixed scrolls (4) is a disk-shaped end plate (4a) on which a spiral (involute) wrap (4b) is erected on one side, and both fixed scrolls (4), (4).
Are arranged so that the wraps (4b) face each other. And these fixed scrolls (4), (4)
An orbiting scroll (6) is arranged between them. This orbiting scroll (6) has a spiral (involute) wrap (6) on each of the upper and lower surfaces of a disk-shaped end plate (6a).
b) is erected, and each wrap (6b)
Are arranged so as to mesh with the wraps (4b) of the opposed fixed scrolls (4), respectively.

An orbiting auxiliary body (7) for holding the orbiting scroll (6) is arranged outside the fixed scrolls (4) and (4). This revolution assisting body (7) has two disk-shaped revolution assisting plates (8), (8) arranged on both upper and lower sides of both fixed scrolls (4), (4). (8) and (8) are both fixed scrolls (4) and (4)
At a lateral position of the fixed scrolls (4) and (4) so as to be able to revolve without interfering with the fixed scrolls (4) and at least at one position in the vertical direction so as not to hinder the inflow of the refrigerant gas from the suction pipe (1a). Are combined. This revolution support plate (8),
(8) The coupling portion is inserted vertically through the through hole (5a) of the portion supporting the fixed scroll (4) in the frame (5), and interferes with the frame (5) during revolution. It is supposed not to. The orbiting scroll (6) is fixed to the orbiting assisting body (7) at at least one of the above-mentioned coupling portions. Further, a cylindrical shaft portion (7b) is provided at the center of the upper surface of the upper revolution support plate (8). The shaft portion (7b) is retained on the top plate portion (5b) of the frame (5) via a bush type eccentric bearing (9) so as to be able to revolve around the shaft center (P). On the other hand, in the center of the lower surface of the lower revolution support plate (8), there is a bottomed cylindrical bearing recess (7) that opens downward.
a) is projected. In this bearing recess (7a), the revolution auxiliary body (7) is engaged with the rotary drive shaft (11) of the drive mechanism section (3) via the crank mechanism (10).

The crank mechanism (10) is a crank shaft portion (11a) formed at the upper end of the rotary drive shaft (11) in which the bearing recess (7a) is fitted through a radial bearing (12). The frame (5) is housed in a recess (5c) provided in the center of a portion of the frame (5) facing the lower surface of the lower fixed scroll (4). The crankshaft portion (11a) has an axial center at a position (Q) that is eccentric in the radial direction from the axial center (P) of the rotary drive shaft (11). Due to this eccentricity, the inner and outer peripheral wall surfaces of the wrap (6b) of the orbiting scroll (6) are wound on the outer peripheral surface and inner peripheral surface of the wrap (4b) of each fixed scroll (4) at a plurality of locations in the spiral direction. The action chambers (13) for contacting and compressing the refrigerant gas between these contact portions are formed on the upper and lower sides of the end plate (6a) of the revolution scroll (6), respectively. Around the lower end of the crankshaft portion (11a), there is a balancer (for canceling the unbalance caused by the revolution movement of the revolution scroll (6) and the revolution assisting body (7) when the rotation drive shaft (11) rotates. 11b) is integrally provided. Further, in this embodiment, the height dimension of the lower working chamber (13) in the axial direction is the upper working chamber (1
3), the effective volume of the lower working chamber (13) is smaller than that of the upper working chamber (13), and the high-pressure refrigerant discharged from the lower working chamber (13) is set. The gas discharge flow rate is made lower than the refrigerant gas discharge flow rate from the upper working chamber (13). The upper and lower working chambers (1
Since the projected areas of 3) and (13) are equal to each other, there is no problem in balancing the thrust load.

The rotary drive shaft (11) is a frame (5).
The upper and lower radial bearings (14) and (15) are rotatably supported around the shaft center (P). The lower part of the rotary drive shaft (11) is fitted into the rotor (16a) of the motor (16) arranged in the lower part of the casing (1), and then extends further downward to provide lubrication provided on the inner bottom part of the casing (1). It has reached the oil sump (17). The stator (16b) of the motor (16) is arranged along the inner wall surface of the casing (1) and is supported and fixed by the frame (5).

Below the lower revolution support plate (8), there is an Oldham mechanism (1) for restricting the rotation of the revolution support body (7).
8) is arranged. The Oldham mechanism (18) has an Oldham ring (19) as shown in FIG. The Oldham ring (19) has a substantially annular shape so as to surround the bearing recess (7a) of the revolution assisting body (7) in a loosely inserted state, and slides by the opening edge of the recess (5c) of the frame (5). It is supported as much as possible. And the Oldham ring (1
Frame keys (19a) slidably contacting the above-mentioned opening edges are provided at two locations of the diametrically opposite portions of 9) so as to project outward in the radial direction. On the other hand, an annular raised portion (20) is formed on the opening edge, and a corresponding frame key (19a) is provided at two portions of the raised portion (20) corresponding to the frame key (19a). A keyway (20a) is provided for guiding slidably only in the disposing direction.
As a result, the Oldham ring (19) is movable only in the direction (vertical direction in FIG. 3) connecting the frame keys (19a) and (19a) with respect to the shaft center (P). Also,
Frame key (19a) of Oldham ring (19),
Scroll keys (19b) are provided so as to project upward at two locations in a direction perpendicular to (19a). on the other hand,
On the lower surface of the revolution drive plate (8), scroll keys (1
9b), the scroll key (1
A key groove (7c) engaging with 9b) is provided in a direction orthogonal to the above-mentioned arrangement direction. Thus, the revolution assisting body (7) can move only in the direction connecting the scroll keys (19b) and (19b) with respect to the Oldham ring (19) (left and right direction in FIG. 3). The Oldham mechanism (18) as described above restricts the revolution assisting body (7) from rotating, and is only capable of revolving around the axis (P). An annular auxiliary thrust bearing (21) slidably in contact with the lower surface of the lower revolution auxiliary plate (8) is provided at the inner peripheral portion of the upper surface of the raised portion (20). .

The upper space in the casing (1) is vertically divided by a top plate portion (5b) as a partition of the frame (5), and the space above the top plate portion (5b) is a high pressure chamber (22).
Further, a space for enclosing both fixed scrolls (4), (4) in the lower part is defined in the low pressure chamber (23). The low pressure chamber (23) is a suction pipe (1) of the casing (1).
a), and is configured to allow the low-pressure refrigerant gas flowing from the suction pipe (1a) to flow into the upper and lower working chambers (13) and (13) via the low-pressure chamber (23), respectively. There is.

The end plate (6) of the orbiting scroll (6)
a) A communication hole (6c) communicating with the upper and lower spaces of the end plate (6a) is provided at the center. A discharge hole (4) for discharging the high-pressure refrigerant gas above the end plate (4a) is formed in the center of the end plate (4a) of the upper fixed scroll (4).
c) is provided. Further, the central portion of the upper revolution support plate (8), that is, the shaft portion (7) of the revolution support body (7).
In b), a discharge hole (7d) for guiding the high pressure refrigerant gas discharged from the discharge hole (4c) to the high pressure chamber (22).
Is provided, the upper end opening of which is provided with an eccentric bearing (9).
It directly faces the high pressure chamber (22) without going through.
The communication hole (6c), the discharge hole (4c) and the discharge hole (7d) form a discharge passage for discharging the high pressure refrigerant gas compressed in the working chamber (13) to the high pressure chamber (22). I am configuring.

On the other hand, a ring-shaped revolving sliding type discharge seal (24) is formed on the upper surface of the end plate (4a) as a discharge hole (4c).
And the lead-out holes (7d) are provided so as to surround the opposite open ends. The discharge seal (24) is provided so as to be in sliding contact with the lower surface of the upper revolution auxiliary plate (8).
By such a discharge seal (24), the discharge passage is partitioned from the low pressure chamber (23) between the upper revolution auxiliary plate (8) and the end plate (4a) of the upper fixed scroll (4). The high pressure chamber (22) communicates with the discharge pipe (1b) of the casing (1), and the high pressure refrigerant gas guided to the high pressure chamber (22) is discharged from the discharge pipe (1b) to the outside. Has been done. In addition, the shaft portion (7b) is held by a crank type eccentric bearing, and the discharge hole (4
The open end on the high pressure chamber (22) side of c) is directly connected to the high pressure chamber (2
In the case where it is difficult to face 2), the eccentric bearing or the like may be provided with a communicating portion that communicates the outlet hole (7d) with the high pressure chamber (22).

Next, the compression operation of the refrigerant gas in the scroll type compressor constructed as described above will be explained. The rotation drive shaft (11) is driven by the operation of the motor (16).
When is rotated, the crankshaft portion (11a) is rotated about the shaft center (P). Along with this, the revolution assisting body (7) makes a similar rotation, but since the rotation is restricted by the Oldham mechanism (18), this rotation becomes a revolution movement around the axis (P). .

With the revolution of the revolution assisting body (7), the revolution scroll (6) revolves with respect to the fixed scrolls (4) and (4). Then, on the upper and lower sides of the end plate (6a) of the orbiting scroll (6), the opposing wraps (6
The contact points of b) and (4b) move toward the center.
With this movement, the upper and lower working chambers (13) are formed between the wraps (6b) and (4b) from the spiral end portion on the outer peripheral side thereof, and these working chambers (13) form a discharge passage in the central portion. The volume decreases while moving toward the spiral.
According to these series of operations, the low-pressure refrigerant gas flows from the suction pipe (1a) into the working chamber (13) through the low-pressure chamber (23) in the casing (1), and each working chamber (13). Due to the decrease in volume, it is compressed to high pressure.

At this time, a load (T) in the thrust direction and a load (R) in the radial direction act on the revolution scroll (6) by the reaction force at the time of gas compression, as shown in FIG. Of these, the thrust loads (T) have opposite directions on the upper and lower sides, so they cancel each other out, and the effect on the orbiting scroll (6) is canceled. On the other hand, although the radial load (R) is smaller than the thrust load (T), it acts to overturn the orbiting scroll (6). However, in this embodiment, the orbiting scroll (6) has a bearing recess (7a) below the orbiting auxiliary body (7).
Is held on the rotary drive shaft (11),
Since the upper shaft portion (7b) of the revolution assisting body (7) is held by the eccentric bearing (9) and is supported at both upper and lower positions of the shaft center (P), both of them are shown in FIG. It is possible to prevent the revolving scroll (6) from overturning due to the overturning moment (M) indicated by a virtual line.

The refrigerant gas that has been compressed in the working chamber (13) and has a high pressure is directed to the discharge hole (4c). However, at this time, the high-pressure refrigerant gas compressed in the lower working chamber (13) first receives passage resistance when passing through the communication hole (6c), and then at the inlet of the discharge hole (4c), the upper working chamber ( 1
It is difficult for the high-pressure refrigerant gas of 3) to enter the discharge hole (4c) and interfere with it. Thus, the lower working chamber (1
The high-pressure refrigerant gas of 3) is likely to be in an over-compressed state under the condition that the discharge resistance is larger than that of the high-pressure refrigerant gas in the upper working chamber (13), which may increase the overall over-compression loss. There is. On the other hand, in this embodiment,
Since the discharge flow rate of the high-pressure refrigerant gas from the lower working chamber (13) is reduced, the above-mentioned overcompression loss can be effectively reduced.

The high pressure refrigerant gas discharged to the discharge hole (4c) is then guided to the high pressure chamber (22) by the discharge hole (7d), but between the discharge hole (4c) and the discharge hole (7d). ,
Since the discharge passage is partitioned from the low pressure chamber (23) by the discharge seal (24) interposed between the upper fixed scroll (4) and the upper revolution auxiliary plate (8), the high pressure refrigerant gas is discharged from the low pressure chamber ( 23) There is no fear of inflow. Then, the high-pressure refrigerant gas flows into the high-pressure chamber (22) and then the discharge pipe (1
It is discharged from b) to the outside.

In the first embodiment, the discharge seal (2
4) is provided slidably in contact with the upper revolution support plate (8), but may be slidably contacted with the end plate (4a) of the upper fixed scroll (4) or both.

(Embodiment 2) FIG. 4 shows a scroll type fluid apparatus according to Embodiment 2 of the present invention. The same parts as those in Embodiment 1 will be described with the same reference numerals. In this embodiment, the scroll mechanism portion (2) is constituted by disposing a double-teeth type fixed scroll (4) between a pair of single-teeth type revolution scrolls (6), (6). There is.

Specifically, the orbiting scroll (6) is formed by vertically arranging a spiral wrap (6b) on one surface of an end plate (6a), and the orbiting scrolls (6), (6) are respectively Are arranged so that the wraps (6b) sides thereof face each other. On the other hand, the fixed scroll (4) has an end plate (4
A spiral wrap (4b) is erected on both sides of a), and between the revolution scrolls (6) and (6),
The wrap (6b) and the respective wraps (4b) of the orbiting scroll (6) facing each other are arranged so as to mesh with each other.

Further, in the revolution support body (7), the end plate (6a) of each revolution scroll (6) is a fixed scroll (4).
Are vertically coupled at a lateral position of the second end of the end plate (6a) of the upper orbiting scroll (6).
And a bearing recess (7a) as a first engaging portion are arranged at the center of the lower surface of the end plate (6a) of the lower revolution scroll (6). . Then, the bearing recess (7a) of the revolution assisting body (7).
Through the crank mechanism (10) to the rotary drive shaft (1
The shaft portion (7b) is retained by the eccentric bearing (9) so as to be able to revolve while being engaged with 1).

Also in this embodiment, when the orbiting scrolls (6) and (6) are revolving, the revolving scrolls (6) and (6) are moved by the reaction force when the refrigerant gas is compressed in the upper and lower working chambers (13). It is possible to cope with the action of the applied radial load (R) to overturn both orbiting scrolls (6), (6), and the overturning moment (M) shown by the phantom line in FIG. 6), (6)
Can be prevented from overturning.

(Third Embodiment) FIG. 5 shows a scroll type fluid device according to a third embodiment of the present invention. The same parts as those in the above-mentioned first embodiment will be described with the same reference numerals.

At the central portion of the upper surface of the end plate (4a) of the upper fixed scroll (4) of the scroll mechanism section (2), the refrigerant gas compressed by the scroll mechanism section (2) into a high pressure is supplied to the high pressure chamber (22). A discharge cylinder (4d) having a discharge hole (4c) for discharging to the upper side is provided so as to project upward, and an upper end portion of the discharge cylinder (4d) is a frame top plate portion (5) as a partition wall.
It penetrates b) and faces the high-pressure chamber (22). The discharge cylinder (4d) supports the upper shaft portion (7b) of the revolution support body (7) through an eccentric bearing (9) so as to be able to revolve around the axis (P). Specifically, the eccentric bearing (9)
Is rotatably held around the axis (P) by the discharge cylinder (4d), and the shaft portion (7b) is rotatably held around the eccentric axis (Q) by the eccentric bearing (9). When the eccentric bearing (9) rotates around the axis (P), the eccentric axis (Q) revolves around the axis (P),
Therefore, the shaft portion (4b) revolves around the shaft center (P).

In this embodiment, in order to cancel the imbalance caused by the orbital movement of the orbiting scroll (6) and the orbiting auxiliary body (7), the eccentric bearing (9) is rotated by an upper balancer (9a). Lower balancers (11b) are provided on the upper ends of the drive shafts (11).

As shown in FIG. 6, the lower balancer (11b) has a predetermined center of gravity (G1) relative to a position having a phase difference of 180 ° with respect to the center of gravity (G) on the revolution assisting body (7) side. Is set to the rear side position in the rotation direction (clockwise direction in the figure) by the phase angle (θ1). Then, as shown in FIG. 7, the amount of eccentricity of the crankshaft portion (11a) with respect to the shaft center (P) of the rotary drive shaft (11), that is, the distance dimension between the shaft center (P) and the eccentric shaft center (Q). L, the crankshaft (11
The clearance between the outer peripheral surface of a) and the inner peripheral surface of the lower bearing portion (7a) of the revolution support body (7) is δ1, and between the crankshaft portion (11a) and the lower bearing portion (7a). If the oil film thickness at H1 is H1, the above phase angle (θ1)
Is determined by the equation represented by θ1 = tan ⁻¹ {(δ1−H1) / L}.

On the other hand, as shown in FIG. 8, the center of gravity (G2) of the upper balancer (9a) has a phase difference of 180 ° with respect to the center of gravity (G) of the revolution assisting body (7). Is set to the front side position in the rotation direction (clockwise direction in the figure) by a predetermined phase angle (θ2). As shown in FIG. 9, the eccentric amount of the eccentric bearing (9) with respect to the shaft center (P) of the rotary drive shaft (11), that is, the distance between the shaft center (P) and the eccentric shaft center (Q), L, the clearance between the outer peripheral surface of the eccentric bearing (9) and the inner peripheral surface of the upper shaft portion (7b) of the revolution auxiliary body (7) is δ2, the eccentric bearing (9) and the upper shaft portion (7b). The oil film thickness between
2, the phase angle (θ2) is defined by the equation represented by θ2 = tan ^-1 {(δ2-H2) / L}.

According to this embodiment, the rotary drive shaft (11)
A balancer (11b), (9a) for canceling the unbalance caused by the revolution movement of the revolution support body (7) and the revolution scroll (6) in both the eccentric bearing and the eccentric bearing (9).
By providing each of them, the above imbalances are balanced off on both sides in the axial center (P) direction of the revolution assisting body (7), so that the accuracy of the dynamic balance can be improved and the vibration can be reduced. . .

The center of gravity (G) of the lower balancer (11b)
1) is 18 with respect to the center of gravity (G) on the revolution auxiliary body (7) side.
A predetermined phase angle (θ
Since only 1) is at the rear side position in the rotation direction, the center of gravity (G1) is positioned at an appropriate position having a phase difference of 180 ° with respect to the center of gravity (G) on the revolution assisting body (7) side during revolution. It will be. In addition, the center of gravity (G2) of the upper balancer (9a) has a predetermined phase angle (θ2) in front of the position having a phase difference of 180 ° with respect to the center of gravity (G) of the revolution assisting body (7). By being in the position, the center of gravity (G2) is positioned at an appropriate position having a phase difference of 180 ° with respect to the center of gravity (G) of the revolution assisting body (7) at the time of revolution. It is possible to further reduce the vibration by improving the accuracy.

In the third embodiment, the case where the two-tooth type revolution scroll (4) is arranged between the pair of one-tooth type fixed scrolls (6) and (6) has been described. Needless to say, the present invention is also applied to the case where the two-tooth type fixed scroll (6) is disposed between the pair of one-tooth type revolving scrolls (4) and (4) as in the second embodiment. .

Although each of the above embodiments has been described with respect to the compressor for the refrigerator, the present invention may be applied to a vacuum pump, an expander or the like. Further, the shape of the revolution assisting body and its respective engaging portions, the eccentric bearing, the crank mechanism, the angle maintaining mechanism, etc. are not limited to those shown in the above-mentioned embodiment, and it goes without saying that known ones can be appropriately adopted. Is.

[0054]

As described above, according to the invention of claim 1 or 2, the orbiting scroll held by the orbiting auxiliary body is supported so as to be able to orbit even on the side opposite to the rotary drive shaft. It is possible to prevent the revolving scroll from overturning due to the radial load, and in combination with using the crank mechanism and angle maintaining mechanism with a simple structure, it is possible to actually balance the thrust load with a relatively simple structure. As a result, it is possible to significantly improve the efficiency.

According to the third aspect of the present invention, the scroll mechanism section in which the two-tooth type revolving scroll is disposed between the pair of fixed scrolls is arranged in the low pressure space in the casing, and in the casing. When an eccentric bearing is rotatably held by a partition wall that divides the low-pressure space and the high-pressure space, a discharge hole is provided in the second engaging portion of the revolution assisting body to discharge the compressed fluid communicating with the high-pressure space. Since the passage is formed and the discharge passage is partitioned from the low pressure space by the sealing material, in the invention of claim 1, the compressed fluid can be discharged to the high pressure space without flowing out to the low pressure space.

According to the fourth aspect of the present invention, the balancers are provided on both sides in the axial direction of the revolution assisting body, respectively, so that the imbalance caused by the revolution movements of the revolution assisting body and the revolution scroll can be offset in a well-balanced manner. It is possible to improve the accuracy of dynamic balance and reduce vibration.

According to the fifth aspect of the present invention, the center of gravity of each of the balancers on both sides is positioned at an appropriate position having a phase difference of 180 ° with respect to the center of gravity of the revolution assisting body during revolution movement. Since the setting is made, it is possible to further reduce the vibration by improving the accuracy of the dynamic balance.

[Brief description of drawings]

FIG. 1 is a schematic view of a main part of a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is a vertical sectional view of a scroll type compressor.

3 is a sectional view taken along line III-III in FIG.

FIG. 4 is a view corresponding to FIG. 1 of a scroll compressor according to a second embodiment of the present invention.

FIG. 5 is a vertical sectional view showing a main part of a scroll compressor according to a third embodiment of the present invention.

FIG. 6 is a diagram showing a phase relationship between the center of gravity of the lower balancer and the center of gravity of the revolution assisting body side.

FIG. 7 is a diagram showing a phase difference between a rotation drive shaft and a revolution support body.

FIG. 8 is a diagram showing a phase relationship between the center of gravity of the upper balancer and the center of gravity of the revolution assisting body side.

FIG. 9 is a diagram showing a phase difference between the eccentric bearing and the revolution assisting body.

FIG. 10 is a schematic view of a main part of a conventional example.

[Explanation of symbols]

 (1) Casing (2) Scroll mechanism part (4) Fixed scroll (4a) End plate (4b) Wrap (4c) Discharge hole (5b) Top plate part (partition wall) (6) Revolution scroll (6a) End plate (6b) Wrap (7) Revolution assisting body (7a) Bearing recess (first engaging part) (7b) Shaft part (second engaging part) (7d) Outlet hole (9) Eccentric bearing (9a) Upper balancer (balancer) (10) Crank mechanism (11) Rotation drive shaft (11b) Lower balancer (balancer) (18) Oldham mechanism (angle maintaining mechanism) (22) High pressure chamber (high pressure space) (24) Discharge seal (seal material) (P) Axial center (G) Center of gravity of the revolution support side (G1) Center of gravity of the lower balancer (G2) Center of gravity of the upper balancer

Claims (5)

[Claims] 1. A pair of fixed scrolls (4) in which spiral wraps (4b) are erected on one side of each end plate (4a),
(4) is arranged so that the wrap (4b) sides face each other, and the end plate (6) is placed between the fixed scrolls (4) and (4).
The orbiting scroll (6) in which spiral wraps (6b) and (6b) are respectively erected on both sides of a) is attached to each wrap (6).
b) is the wrap (4) of the opposing fixed scroll (4)
b) and the fixed scroll (4) and the revolution scroll (6) are arranged so as to mesh with each other, and constitute a scroll mechanism section (2) for compressing and discharging the fluid. ) In the scroll type fluid device in which the revolution scroll (6) is revolved around the axis (P) while restricting the rotation of the revolution scroll (6) on the rear side of the end plate (4a) of each fixed scroll (4). Revolving auxiliary body (7) having first and second engaging portions (7a) and (7b) positioned and holding the revolving scroll (6) is provided on both fixed scrolls (4) and (4). The revolving auxiliary body (7) is reciprocally provided so that the first engaging portion (7a) of the revolving auxiliary body (7) is engaged with the rotary drive shaft (11) through the crank mechanism (10), while the second engaging portion (7) is engaged. Eccentricity that holds the joint (7b) so that it can revolve A scroll type fluid device comprising a bearing (9) and an angle maintaining mechanism (18) for enabling the revolution assisting body (7) to revolve while restricting its rotation. 2. A pair of orbiting scrolls (6) in which spiral wraps (6b) are erected on one side of each end plate (6a),
(6) are arranged so that the wrap (6b) sides face each other, and the end plate (4) is placed between the orbiting scrolls (6) and (6).
The fixed scroll (4) in which spiral wraps (4b) and (4b) are respectively installed upright on both sides of a) is attached to each wrap (4).
b) is the wrap (6) of the orbiting scroll (6)
b) and the orbiting scroll (6) and the fixed scroll (4), which are arranged so as to mesh with each other, constitute a scroll mechanism section (2) for compressing and discharging the fluid, and the rotary drive shaft (11). In the scroll type fluid device in which both orbiting scrolls (6) and (6) are revolved around the axis (P) while restricting their rotation in accordance with the driving of (1), the end plate (6a) of each orbiting scroll (6). ) Has a first and a second engaging portion (7a), (7b) located on the back side of the orbiting auxiliary body (7) holding the orbiting scroll (6), the fixed scroll (4). The revolving auxiliary body (7) is reciprocally provided so that the first engaging portion (7a) of the revolving auxiliary body (7) is engaged with the rotary drive shaft (11) through the crank mechanism (10), while the second engaging portion (7) is engaged. Eccentricity that holds the joint (7b) so that it can revolve A scroll type fluid device comprising a bearing (9) and an angle maintaining mechanism (18) for enabling the revolution assisting body (7) to revolve while restricting its rotation. 3. The scroll type fluid device according to claim 1, wherein the internal space of the casing (1) accommodating the scroll mechanism portion (2) is a low-pressure space (a space for disposing the scroll mechanism portion (2)). 23) and a high-pressure space (22), which is a discharge space of the high-pressure fluid compressed by the scroll mechanism portion (2), are partitioned by a partition wall (5b), and the partition wall (5b) partitions the second engagement portion (7b). ) Is rotatably held, and a discharge hole (4c) communicating with both side spaces of the end plate (4a) is provided at the center of the end plate (4a) of the fixed scroll (4) located on the side of the eccentric bearing (9). The second engaging portion (7b) is provided with a lead-out hole (7d) for communicating the discharge hole (4c) with the high-pressure space (22), and between the revolution assisting body (7) and the end plate (4a). The annular seal that can be slidably contacted with at least one of the two. Wood scroll fluid device being characterized in that interposed so as to surround the opposite open end (24) of the lead-out hole (7d) and the discharge hole (4c). 4. The scroll type fluid device according to claim 1 or 2, wherein a revolution assisting body (7) is provided on an end of the rotary drive shaft (11) on the first engaging portion (7a) side and the eccentric bearing (9). ) And balancers (11b) and (9a) for canceling the unbalance caused by the orbital movement of the orbiting scroll (6), respectively. 5. The scroll type fluid device according to claim 4, wherein the center of gravity (G) of the balancer (11b) of the rotary drive shaft (11) is used.
1) is 18 with respect to the center of gravity (G) on the revolution auxiliary body (7) side.
A predetermined phase angle (θ
Only 1) is at the rear position in the rotational direction, and the center of gravity (G2) of the balancer (9a) of the eccentric bearing (9)
Is 180 ° with respect to the center of gravity (G) on the revolution auxiliary body (7) side.
A scroll type fluid device characterized in that the scroll type fluid device is located at a position on the front side in the rotation direction by a predetermined phase angle (θ2) with respect to the position having the phase difference.