JPH0835492A - Co-rotating scroll fluid machine - Google Patents

Abstract

PURPOSE:To reduce one side hitting of a driven shaft to a bearing part even when a drive shaft is inclined at the time of rotary driving. CONSTITUTION:The scroll hydraulic machine in the title is provided with a drive scroll 2 and a driven scroll 4 and the drive scroll side end part of the drive shaft 1 is bearing supported by a first bearing part 91 and the opposite drive scroll side end part of the drive shaft 1 is bearing supported by a second bearing part and the driven shaft 3 is bearing supported by a third bearing part 93 (a, b) bearing supported eacentrically in relation to the axial center of the drive shaft 1. An initial inclination is given to the third bearing part 93 (a, b) in the direction same as the inclination direction of the driven shaft 3 inclined by a load acting to the scroll body 42 of the driven scroll 4 by the hydraulic pressure in a scroll chamber 63.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a co-rotating scroll fluid machine.

[0002]

2. Description of the Related Art Conventionally, there has been provided a scroll element portion composed of a drive scroll having a drive shaft protruding therefrom and a driven scroll having a driven shaft protruding therefrom, and the driven shaft being eccentric with respect to the drive shaft of the drive scroll. A co-rotating scroll fluid that is rotatably supported, rotates the drive scroll with the rotation of the drive shaft, and causes the driven scroll to follow with the rotation of the drive scroll around the driven shaft. As a machine, for example, one described in Japanese Patent Application Laid-Open No. 4-76287 is known.

This co-rotating scroll fluid machine is shown in FIG.
As shown in FIG. 5, the drive scroll 2 integrally formed in the shaft end of the drive shaft 1 connected to the motor M in the closed casing A, and rotated at a position eccentric to the shaft center of the drive shaft 1. A driven scroll 4 having a driven shaft 3 that is movably supported, an axial direction regulating member 5, and a scroll element portion 6 including a transmission joint 61 are internally provided.
Reference numeral 4 includes end plates 21 and 41 and spiral members 22 and 42 projecting from the end plates 21 and 41.
In a state where they are meshed with each other, further on the back side of the driven scroll 4, the axial direction regulating member 5 and the transmission joint 6 are provided.
1 are overlapped with each other, and the scrolls 2, 4, the axial direction regulating member 5, and the transmission joint 61 are sandwiched by a plurality of U-shaped pieces 62, and as the drive scroll 2 is rotationally driven by the drive shaft 1, The driven scroll 4 is swung while being driven and rotated via the transmission joint 61 to compress, for example, the fluid taken into the spiral chamber 63 formed between the spiral bodies 22 and 42.

The drive shaft 1 has a drive side support member 7
The first bearing portion 91 bearing-supports the end portion of the drive shaft 1 on the drive scroll side, and the end portion of the drive shaft 1 on the side opposite to the drive scroll is disposed on the side opposite to the scroll element of the motor M.
The driven shaft 3 is supported by a bearing portion (not shown), and the driven shaft 3 is supported by the third bearing portion 93 of the driven side support member 8.

[0005]

In the conventional co-rotating scroll fluid machine, the drive scroll 2 is rotatably supported by the first bearing portion 91 and the second bearing portion via the drive shaft 1. Since the driven scroll 4 is rotatably supported by the third bearing portion 93 via the driven shaft 3, the fluid pressure in the spiral chamber 63 is increased by the rotational drive of the drive shaft 1. The drive shaft 1 is acted on the second and fourth spiral bodies 22 and 42 by the load due to the fluid pressure, and the first drive shaft 1 is rotated by the first drive shaft 1.
An inclination occurs in the range of the bearing gap between the bearing portion 91 and the second bearing portion 92, and the drive scroll 2 and the driven scroll 4 are sandwiched by a plurality of U-shaped pieces 62 via the axial direction regulating member 5. As a result, the driven shaft 3 also tilts within the range of the bearing clearance of the third bearing portion 93.

That is, as shown in FIG. 16, in the scroll chamber 63 formed by the scrolls 22, 42, the fluid pressure is compressed by the action of the scrolls 2 and 4 of the scrolls 2 and 4.
2, 42, so that the drive scroll 2
If the center of the basic circle of the spiral body 22 is O ₁ and the center of the basic circle of the spiral body 42 of the driven scroll 4 is O ₂ , the spiral body 22 of the drive scroll 2 has a center O ₁ of the drive scroll 2. Starting from a midpoint on a line segment connecting the base circle center O ₂ of the driven scroll 4 with the base circle, a radial gas load (force for increasing the gap between spirals) Fr accompanying gas compression.
′ And a tangential gas load (resistance force when the drive scroll 2 rotates in the x direction facing the gas pressure in each spiral chamber 63 formed by each spiral body 22, 42) Ft ′, The combined force of these loads Fr ′ and Ft ′ becomes a gas load F ′ (not shown) that acts on the scroll 22 of the drive scroll 2.

The scroll 42 of the driven scroll 4 is also used.
The, as a starting point the midpoint on a line connecting the base circle center O ₂ of the base circle center O ₁ and the driven scroll 4 of the drive scroll 2, caused by gas compression, the radial gas load (spiral between gap Force to increase) Fr and tangential gas load (resistance force when the driven scroll 4 rotates in opposition to the gas pressure in each spiral chamber 63 formed by each spiral body 22 and 42) Ft. Therefore, the radial gas load Fr has the same magnitude as the radial gas load Fr ′ of the drive scroll 2 and has the opposite direction, and the tangential gas load Ft is also equal to that of the drive scroll 2. The magnitude is the same as the tangential gas load Ft ', but the direction is opposite.

Further, the combined force of these loads Fr and Ft becomes a gas load F (not shown) acting on the scroll 42 of the driven scroll 4.

Further, as shown in the basic structure of the scroll element portion 6 in FIG. 14, the drive shaft 1 is supported by the first bearing portion 91 when the first bearing portion 91 is a slide bearing. The first shaft bearing portion 91 and the drive shaft 1
And the overall clearance C ₁₁ between them and the inner diameter of the first bearing portion 91 is D ₁₁ , and the outer diameter of the portion of the drive shaft 1 supported by the first bearing portion 91 is d ₁₁ .

[0010]

Equation 3] through C ₁₁ = total clearance C ₁₁ represented by the formula D ₁₁ -d ₁₁ is a bearing support, to the second bearing portion 92 also sliding bearings, also in the second bearing portion 92 , The second bearing portion 92 and the drive shaft 1
And a total clearance C ₁₂ between them, that is, an inner diameter of the second bearing portion 92 is D ₁₂ , and an outer diameter of a portion of the drive shaft 1 supported by the second bearing portion 92 is d ₁₂ ,

[0011]

## EQU4 ## The bearing is supported via the entire clearance C ₁₂ represented by the formula C ₁₂ = D ₁₂ -d ₁₂ .

Further, the driven shaft 3 has the third bearing portion 9
When 3 is also a plain bearing, when the bearing is supported by the third bearing portion 93, the entire clearance C ₂ between the third bearing portion 93 and the driven shaft 3, that is, the third bearing portion 93. Let D _{21 be} the inner diameter of the driven shaft 3 and d ₂₁ be the outer diameter of the portion of the driven shaft 3 supported by the third bearing portion 93.

[0013]

## EQU5 ## The bearing is supported through the entire clearance C ₂ represented by the formula C ₂ = D ₂₁ -d ₂₁ .

As a result, the length from the drive scroll side end of the first bearing portion 91 to the counter drive scroll side end of the second bearing portion 92 is the bearing length L ₁ of the drive shaft 1. Therefore, the drive shaft 1 is rotationally driven, and the action of the gas load F ′ on the scroll body 22 of the drive scroll 2 causes

[0015]

[Equation 6] α ₁ = (C ₁₁ + C ₁₂ ) / 2L ₁ Maximum allowable inclination α ₁ by each bearing 91, 92
It will tilt up to the range.

Therefore, as shown in FIG. 14, when the drive shaft 1 comes into contact with the drive scroll side end of the first bearing portion 91 and the anti-scroll side end of the second bearing portion 92,
It will tilt to the maximum.

Further, the driven shaft 3 also has the third bearing portion 9
Since the bearing is supported by the bearing 3 through the bearing clearance C ₂ , as shown in FIG. 14, the length L of the third bearing portion 93 is L.
_{Since 2} is the bearing length, when the driven shaft 3 rotates in accordance with the rotational drive of the drive shaft 1, the driven shaft 3 is acted on by the action of the gas load F on the scroll 42 of the driven scroll 4,

[0018]

[Formula 7] α ₂ = C ₂ / L ₂ Maximum allowable inclination α ₂ by the third bearing portion 93
It will tilt up to the range.

Therefore, when the driven shaft 3 is tilted up to the allowable maximum tilt α ₂ , the driven shaft 3 is moved to the third position.
The bearing portion 93 comes into contact with both ends thereof.

Considering when the drive shaft 1 is rotationally driven, the drive shaft 1 is not only subjected to the inclination of the rigid body, but also a moment due to fluid pressure acts on the drive shaft 1. Is bent by elastic deformation, and when this bending is large, the driven shaft 3 tends to tilt more than the allowable maximum tilt α ₂ in accordance with the bending of the drive shaft 1, and the driven shaft 3 is bent by the third bearing portion. There has been a problem that the driven shaft 3 is damaged due to a strong one-sided contact with 93.

Further, as shown in FIG. 14, one end plate 21 or 41 of the driving scroll 2 or the driven scroll 4 and the other driven scroll 4 or the driving scroll 2 are fixed to the scroll 4 or 2. In the case of a holding structure sandwiched by the axial direction regulating member 5, as shown in FIG. 14, when the held scroll is, for example, the driven scroll 4, the driven scroll 4 is rotated by the drive scroll 2. The end plate 41 is interposed between the drive scroll 2 and the axial direction regulating member 5 with a predetermined gap δ with respect to the axial direction regulating member 5 so that the end plate 41 can freely rotate. Therefore, if the diameter of the driven scroll 4 is D,
The driven scroll 4 tilts up to a tilt δ / D with respect to the drive scroll 2 and the axial direction regulating member 5.

Therefore, when the driven scroll 4 is tilted by a maximum of δ / D with respect to the drive scroll 2, the driven shaft 3 is tilted more than the tilt of the drive shaft 1 as shown in FIG. Therefore, the driven shaft 3 is inclined to the allowable maximum inclination α ₂ only by the inclination of the rigid body, and the driven shaft 3 causes a stronger one-sided contact with the third bearing portion 93 to cause the driven shaft 3 to move. The problem that the shaft 3 is broken occurs.

In the above-mentioned conventional example, the problem of the slide bearing was described as a bearing, but a rolling bearing including an inner ring, an outer ring and rollers is also interposed between the inner ring and the outer ring and the inner ring / outer ring. For mounting a predetermined clearance between the roller and the rolling bearing, the outer ring is press-fitted to the bearing unit side, or the inner ring is press-fitted and fixed to the drive shaft 1 or the driven shaft 3 to fix the bearing unit. Since it is supported by the bearings, the bearings are supported with a predetermined gap between each shaft and the bearing unit. This causes a problem of contact, and in the case of a rolling bearing, a partial contact occurs between the inner ring and the inner ring and the life of the bearing is shortened.

The present invention has been made to solve the above problems, and an object thereof is to reduce uneven contact of a driven shaft with a bearing portion even when the drive shaft is inclined during rotational driving, and
This is to prevent the life of the bearing portion from being shortened.

[0025]

In order to achieve the above object, the present invention according to claim 1 provides a drive scroll 2 having a mirror plate 21 provided with a scroll 22 and a drive shaft 1.
And a driven scroll 4 having a driven shaft 3 and an end plate 41 projecting a scroll 42 that meshes with the scroll 22 of the drive scroll 2 to form a scroll chamber 63, and the drive scroll side of the drive shaft 1 is provided. The end portion is bearing-supported by the first bearing portion 91, the position of the drive shaft 1 away from the drive scroll 2 is bearing-supported by the second bearing portion 92, and the driven shaft 3 is the axial center of the drive shaft 1. In the co-rotating scroll fluid machine bearing supported by a third bearing portion 93 which is eccentrically supported, the driven shaft 3 tilted by the load acting on the scroll body 42 of the driven scroll 4 by the fluid pressure in the scroll chamber 63. The initial inclination θ is given to the third bearing portion 93 in the same direction as the inclination direction.

According to a second aspect of the present invention, the first bearing portion 9 is provided.
The total clearance between the drive shaft 1 and the drive shaft 1 is C ₁₁ , the second bearing portion 92
When the total gap between the drive shaft 1 and the first bearing portion 91 is C ₁₂ , the inter-bearing length between the first bearing portion 91 and the second bearing portion 92 is L ₁ , and the initial inclination of the third bearing portion 93 is θ. , This initial slope θ
To

[0027]

[Formula 1] θ> (C ₁₁ + C ₁₂ ) / 2L ₁ is set so as to satisfy the condition.

According to a third aspect of the present invention, one of the driving scroll 2 and the driven scroll 4 is provided with an axial direction regulating member 5.
And the other scroll 4 or 2 is housed in the space 64 formed by the one scroll 2 or 4 and the axial direction regulating member 5, and the initial inclination of the third bearing portion 93 is θ, End plate 4 of the other scroll 4 or 2
1 or 21 and the axial direction regulating member 5 is δ in the axial direction, the diameter of the end plate 41 or 21 of the other scroll 4 or 2 is D, and between the drive shaft 1 of the first bearing portion 91. total clearance C ₁₁ of the entire clearance a C _12, the entire clearance C ₂ between the driven shaft 3 of the third bearing portion 93 between the drive shaft 1 of the second bearing portion 92, the first The inter-bearing length between the bearing portion 91 and the second bearing portion 92 is L ₁ , and the third bearing portion 9 is
When the length of 3 is L ₂ , the inclination δ / D of the one scroll 2 or 4 and the other scroll 4 or 2 with respect to the axial direction regulating member 5 is

[0029]

[Number 2] _{δ / D <C 2 / L} 2 - (C 11 + C 12) / 2L 1 + the initial inclination so as to satisfy the condition theta is The defined theta.

According to a fourth aspect of the present invention, the third bearing portion 9 is provided.
3, a driven side support member 8 provided on the driven scroll 4 side.
In addition, it is possible to swing according to the load acting on the scroll body 42 of the driven scroll 4 due to the fluid pressure of the scroll chamber 63 compressed by the meshing of the scroll bodies 22 and 42 of the scrolls 2 and 4, and the shaft. There is provided a pressing means that movably supports the scrolls 2 and 4 and presses the side surfaces of the scrolls 22 and 42 of the scrolls 2 and 4 against each other.

According to a fifth aspect of the present invention, the third bearing portion 9 is provided.
3, a driven side support member 8 provided on the driven scroll 4 side.
In addition, the scrolls 22 and 42 of the scrolls 2 and 4 are slidable according to the load acting on the scroll 42 of the driven scroll 4 due to the fluid pressure in the scroll chamber 63 compressed by the meshing of the scrolls 22 and 42, and the slide width is slidable. There is provided a pressing means that supports the scrolls 2 and 4 in the axial direction so as to be movable in the axial direction through a predetermined gap, and presses the side surfaces of the scrolls 22 and 42 of the scrolls 2 and 4 against each other.

[0032]

According to the first aspect of the present invention, even if the drive shaft 1 is tilted by rotational driving, the third bearing portion 93 bearing-supporting the driven shaft 3 is provided with the third bearing portion 93 due to the fluid pressure in the spiral chamber 63. Since it can be preliminarily tilted in the same direction as the tilting direction of the driven shaft 3 which is tilted by the load acting on the scroll 42 of the driven scroll 4, it is possible to reduce strong uneven contact at the third bearing portion 93 of the driven shaft 3. And the third bearing portion 9
3 can be prevented from being damaged and reliability can be improved.

According to the second aspect of the present invention, the holding structure is set by setting it so as to be larger than at least the maximum inclination α ₁ at the time of rotational driving of the drive shaft 1 shown in Expression 6, as shown in Expression 1. If the bending due to the elastic deformation is small, the driven shaft 3 will not be unidirectionally contacted with the third bearing portion 93 only by the inclination of the drive shaft 1. Therefore, the unidirectional contact of the driven shaft 3 will be prevented. This can be surely prevented, and the durability of the third bearing portion 93 can be improved.

In the invention of claim 3, in the case of the holding structure, the initial inclination θ is set so as to satisfy the condition of the mathematical expression 2,

[0035]

[Equation 10] When the initial inclination θ is set so as to satisfy the formula δ / D ≧ C ₂ / L ₂ − (C ₁₁ + C ₁₂ ) / 2L ₁ , the other scroll 4 or 2 end plate Since the axial gap δ between 41 or 21 and the axial regulating member 5 can be increased, the degree of freedom in designing the scrolls 2 and 4 can be increased.

According to a fourth aspect of the invention, the spiral chamber 63
The third bearing portion 93 can be swung in the direction in which the spiral bodies 22 and 42 are pressed against each other with respect to the driven side support member 8 in accordance with the load due to the fluid pressure. Scrolls 2 and 4 scrolls 22 and 4
The clearance between the two side surfaces can be controlled, and the third bearing portion 93 can be tilted according to the tilt of the driven shaft 3, so that the third bearing portion 93 is tilted according to the tilt of the driven shaft 3.
It is possible to favorably prevent the bearing portion 93 from evenly hitting.

In the invention according to claim 5, the spiral chamber 63 is provided.
Since the third bearing portion 93 can be slid in the direction in which the spiral bodies 22, 42 are pressed against each other with respect to the driven side support member 8 in accordance with the load due to the fluid pressure of
By this slide, the clearance between the side surfaces of the spiral bodies 22, 42 can be controlled, and further, the third bearing portion 93 can be tilted in accordance with the tilt of the driven shaft 3, so that the driven shaft can be tilted. The third bearing portion 9 due to the inclination of 3
It is possible to favorably prevent uneven contact of 3 as well.

[0038]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG. The first embodiment shown in FIG. 1 is applied to a scroll compressor as a co-rotating scroll fluid machine,
This compressor incorporates a co-rotating scroll element portion 6 supported by a drive-side support member 7 and a driven-side support member 8 on one side in the longitudinal direction of a horizontal hermetic casing A, and at the same time, in the longitudinal direction inside the casing A. A motor (not shown) is arranged on the other side in the direction.

The scroll element portion 6 is coupled to the motor and is not shown in FIG. 1 and the first bearing portion 91 of the drive side support member 7, but as shown in FIG. The drive shaft 1 supported by the bearing portion 92 is integrally projected, and the drive scroll 2 has an end plate 21 on which the spiral body 22 is protruded on the side opposite to the drive shaft, and the drive shaft 2 has an axial center. The driven shaft 3 supported by the third bearing portion 93 on the driven-side support member 8 at a position eccentric to the driven shaft 3 projects from the driven shaft 3. The spiral body meshes with the scroll 22 of the drive scroll 2 on the side where the driven shaft does not project. The driven scroll 4 has an end plate 41 on which 42 is provided.

Further, the end plate 21 of the drive scroll 2 is used.
On the outer peripheral portion of the scroll body 22, a buildup portion 23 having substantially the same height as the scroll body 22 is provided so as to project, and the scroll bodies 22 and 42 of the scrolls 2 and 4 are meshed with each other. 23, the axial direction regulating member 5 arranged on the back side of the end plate 41 of the driven scroll 4 is attached to the driven scroll 4
Also, a transmission joint 61 composed of an Oldham's joint is sandwiched, and the driven scroll 4 is driven to rotate while the driven scroll 4 is driven by the drive joint 2 via the transmission joint 61.

Then, the scroll element portion 6 composed of each of the scrolls 2 and 4 is housed in a housing chamber 71 formed by the driving side supporting member 7 and the driven side supporting member 8 and is housed in the housing chamber 71. The suction pipe 65 is opened so that the gas flowing from the suction pipe 65 is introduced into the accommodation chamber 71.

A discharge port 24 is opened in the center of the end plate 21 of the drive scroll 2, and the discharge port 24 is communicated with a discharge passage 11 penetrating the drive shaft 1. By opening the discharge passage 11 into the casing inner space, the gas compressed in the scroll element portion 6 is discharged from the discharge passage 11 to the casing inner space.

Therefore, in the above construction, when the drive scroll 2 is rotationally driven via the drive shaft 1 as the motor rotates, the driven shaft 3 is driven while the driven scroll 4 is driven. And the gas introduced from the suction pipe 65 into the accommodation chamber 71 formed by the driving side support member 7 and the driven side support member 8 is moved between the scrolls 2 and 4 by the swirling motion about the The compressed high-pressure gas is discharged from the discharge port 24 provided in the drive scroll 2 to the internal space of the casing via the discharge passage 11 in the drive shaft 1. is there.

However, in the first embodiment of FIG. 1, the third bearing portion 93 for eccentrically bearing the driven shaft 3 with respect to the axis of the drive shaft 1 is formed separately from the driven side support member 8. Initially, in the same direction as the inclination direction of the driven shaft 3 inclined to the third bearing portion 93 by the load (gas load F) acting on the spiral body 42 of the driven scroll 4 due to the fluid pressure of the spiral chamber 63. The inclination θ is given.

Specifically, when the driven shaft 3 of the driven scroll 4 is rotationally driven, the tip end of the driven shaft 3 is directed in the anti-gas load direction by the gas load F acting on the spiral body 42 of the driven scroll 4. The third bearing portion 93
Is composed of a cylindrical portion 93a for receiving the driven shaft 3 of the driven scroll 4 and a mounting seat 93b for mounting the driven side supporting member 8 on the driven side supporting member 8. The mounting seat 93b is provided between the back surface of the mounting seat 93b and the driven-side support member 8 so as to give a predetermined initial tilt θ in advance in accordance with the tilt of the shaft 3 during rotational driving. It is fixed to the driven side support member 8 with 94 interposed.

Then, as shown in FIG.
And as shown in Formula 4, the total clearance between the first bearing portion 91 and the drive shaft 1 is C ₁₁ , the total clearance between the second bearing portion 92 and the drive shaft 1 is C ₁₂ , The first bearing portion 9
1 from the end portion on the drive scroll side to the end portion on the non-drive scroll side of the second bearing portion 92, that is, each first bearing portion 9
When the inter-bearing length between the first bearing portion 92 and the second bearing portion 92 is L ₁ ,
The initial inclination θ of the third bearing portion 93 is at least the above-mentioned mathematical expression 6
As shown in, the drive shaft 1 is designed to be larger than the maximum inclination α ₁ at the time of rotational drive, that is,

[0047]

[Equation 1] θ> (C ₁₁ + C ₁₂ ) / 2L ₁ is set so as to satisfy the condition. In the first embodiment, as shown in FIG. 2, the mounting of the third bearing portion 93 is performed. The length from the fixing portion of the seat 93b to the driven-side support member 8 to the mounting position of the plate-shaped member 94 is d ₁ .
If the thickness of the plate member 94 is t ₁ ,

[0048]

[Formula 8] θ = (t ₁ / d ₁ )> (C ₁₁ + C ₁₂ ) / 2L ₁ so that the length d ₁ and the plate-shaped member 94 are satisfied.
The initial inclination θ is given by setting the thickness t ₁ of the.

Further, in the first embodiment, the axial direction regulating member 5 is integrally connected to the drive scroll 2, and the driven scroll is inside the space 64 formed by the drive scroll 2 and the axial direction regulating member 5. 4 has an internal structure, the initial inclination of the third bearing portion 93 is θ, the end plate 41 of the driven scroll 4 and the axial direction regulating member 5 are included.
And δ, the diameter of the end plate 41 of the driven scroll 4 is D, and the entire gap between the first bearing portion 91 and the drive shaft 1 is represented by Equations 1 to 5. The clearance is C ₁₁ , the overall clearance between the second bearing portion 92 and the drive shaft 1 is C ₁₂ , the overall clearance between the third bearing portion 93 and the driven shaft 3 is C ₂ , and the first clearance is C ₂ . When the inter-bearing length between the bearing 91 and the second bearing 92 is L ₁ and the length of the third bearing 93 is L ₂ , the driven scroll 4 with respect to the drive scroll 2 and the axial direction regulating member 5 is shown. Slope of δ / D
And the deflection α ₃ due to elastic deformation of the scrolls 2 and 4 due to the moment action of the gas loads F ′ and F is further added to the maximum inclination α ₁ of the drive shaft 1 in the mathematical expression 6, the initial inclination θ is , Taking into consideration the maximum inclination α ₂ of the driven shaft 3 in Equation 7,

[0050]

[Equation 9] It is preferable to satisfy θ <(C ₁₁ + C ₁₂ ) / 2L ₁ + C ₂ / L ₂ + δ / D + α ₃ .

As described above, in the first embodiment, the third bearing portion 93 for eccentrically bearing the driven shaft 3 with respect to the axis of the drive shaft 1 is formed separately from the driven side support member 8. Initially, in the same direction as the inclination direction of the driven shaft 3 inclined to the third bearing portion 93 by the load (gas load F) acting on the spiral body 42 of the driven scroll 4 due to the fluid pressure of the spiral chamber 63. Since the inclination θ is given, even if the drive shaft 1 is inclined due to rotational driving, the third bearing portion 93 bearing-supporting the driven shaft 3 causes the load F of the driven shaft 3 to be applied.
Since it can be preliminarily tilted in accordance with the inclination due to, it is possible to reduce strong uneven contact of the driven shaft 3 at the third bearing portion 93 and prevent damage to the third bearing portion 93, thus improving reliability. You can do it.

In particular, the initial inclination θ is set to be larger than at least the maximum inclination α ₁ at the time of rotational driving of the drive shaft 1 shown in the equation 6 as shown in the equation 1, so that the holding In the case where the driven shaft 3 is not structured and the bending due to elastic deformation is small, the driven shaft 3 does not hit the third bearing portion 93 only by tilting the drive shaft 1. Can be reliably prevented, and the durability of the third bearing portion 93 can be improved.

In the first embodiment, the mounting seat 93b is used.
The mounting seat 93b is attached to the driven-side support member 8 so as to give a predetermined initial inclination θ to the inclination of the driven shaft 3 when the driven shaft 3 is rotationally driven.
The plate-shaped member 94 is fixed to the driven-side support member 8 with the plate-like member 94 interposed between the rear surface and the driven-side support member 8. However, as in the second embodiment shown in FIG. Is provided outside the accommodating chamber 71 formed by the driving side support member 7 and the driven side support member 8, and the surface of the mounting seat 93b on the driven scroll 4 side and the driven side support member 8 are provided. The plate-shaped member 94 may be interposed between the two.

In the second embodiment, the driven shaft 3 of the driven scroll 4 is formed in a tubular shape, and the third bearing portion 93 is used.
In addition, a shaft portion 93c to be inserted and fitted into the cylindrical driven shaft 3 is formed.

Next, a third embodiment will be described with reference to FIGS. In the third embodiment, the third bearing portion 93 is used.
Is provided on the driven scroll 4 side, and the driven side support member 8 is provided.
In addition, the scrolls 2 and 4 are supported so as to be swingable and axially movable in accordance with the load due to the fluid pressure of the spiral chamber 63 compressed by the meshing of the spiral bodies 22 and 42. A pressing means for pressing the spiral bodies 22 and 42 of 2 and 4 against each other is provided.

Specifically, the third bearing portion 93 is a cylindrical portion 93a for receiving the driven shaft 3 of the driven scroll 4.
And a mounting seat 93b on which the cylindrical portion 93a is projected. The mounting seat 93b is fitted with a support shaft 81 projecting toward the scroll element portion 6 side on the driven side support member 8. Swing piece 93e having a shaft hole 93d and a support piece 9 extending in the radial direction on the opposite side of the swing piece 93e by 180 degrees.
3f, a supporting shaft 81 is fitted into a shaft hole 93d of the swinging piece 93e, and the supporting shaft 81 is movable on the driven side supporting member 8 and the mounting seat 93b is movable in the axial direction. a predetermined gap t _2, and, by receiving the mounting seat 93 b, so that mounting to support so as not to fall out.

[0057] Further, as shown in FIG. 4, O ₁ a basic circle center of the spiral body 22 of the driving scroll 2, when the base circle center of the spiral body 42 of the driven scroll 4 and O _2, to the driven scroll 4 , The center O of the base circle of the drive scroll 2
Starting from the midpoint on the line segment connecting ₁ and the center O ₂ of the base circle of the driven scroll 4, the radial gas load (force for increasing the inter-spiral gap) Fr and the tangential gas accompanying the gas compression are set as the starting points. Load (when the driven scroll 4 faces x against the gas pressure in each spiral chamber 63 formed by each spiral body 22 and 42)
Direction resistance force Ft), and the resultant load of these loads Fr, Ft is the gas load F acting on the driven scroll 4, and the support shaft 8
1 is a counter-base circle center O ₁ side from the action line of the gas load F through the midpoint of the line segment connecting the base circle center O ₂ of the base circle center O ₁ and the driven scroll 4 of the drive scroll 2 , Provided on the side opposite to the gas load direction.

When the gas load F acts, the third bearing portion 93 causes the support shaft 81 to move in the anti-gas load direction on the anti-base circle center O ₁ side from the line of action of the gas load F. Since it is provided, centering around the support shaft 81,
Since the center O ₂ of the basic circle of the driven scroll 4 swings in the direction away from the center O ₁ of the basic circle of the drive scroll 2, the spiral bodies 22 and 42 act so as to press each other. Thus, the spiral bodies 22 and 42 can be reliably sealed.

Moreover, the third bearing portion 93 is attached to the driven side support member 8 via the support shaft 81 in a cantilevered manner, and moves in the axial direction within the range of the predetermined clearance t _2. Therefore, the third bearing portion 9
3, when the driven shaft 3 is supported by a bearing, and when the operation is stopped,
Since the driven shaft 3 is straight, the third bearing portion 93 is positioned such that the entire mounting seat 93b is separated from the driven-side support member 8 by the predetermined gap t ₂ .
After that, when the driven shaft 3 tilts due to the rotational driving, the third bearing portion 93 causes the gap t to follow the tilt.
It will tilt in the range of ₂ .

The inclination at this time is defined as an initial inclination θ, and the initial inclination θ is determined by the inclination of the third bearing portion 93 when the supporting piece 93f on the mounting seat 93b is arranged as shown in FIG. Assuming that the point of contact with the driven-side support member 8 is a support point e, as shown in FIG.
The inclination (t ₂ / d ₂ ) obtained by the length d ₂ from the center of the support shaft 81 to the center of the support shaft 81 and the predetermined gap t ₂ is the maximum inclination, and when the maximum inclination is the initial inclination θ, This initial inclination θ is set so as to satisfy the equations 1 and 9 as in the first embodiment.

As described above, in the third embodiment, the third
On the driven side support member 8 provided with the bearing portion 93 on the driven scroll 4 side, the scrolls 22, 4 of the scrolls 2, 4 are provided.
The scrolls 22 and 42 in the scrolls 2 and 4 are supported so as to be swingable and axially movable according to the load of the fluid pressure of the spiral chamber 63 compressed by the meshing of two.
Since the pressing means for pressing the side surfaces of the scrolls 2 and 4 against each other is provided, the third bearing portion 93 can be controlled in accordance with the inclination of the driven shaft 3 while controlling the clearance between the side surfaces of the scrolls 22 and 42 of the scrolls 2 and 4. Since it is possible to tilt the driven shaft 3, it is possible to further prevent uneven contact of the third bearing portion 93 due to the tilt of the driven shaft 3.

Next, a fourth embodiment will be described with reference to FIGS. 6 and 7. In the fourth embodiment, similar to the third embodiment, the third bearing portion 93 is swingably supported by the driven-side support member 8, but in the fourth embodiment, the driven-side support is provided. the gas position of the support shaft 81 passes through the midpoint of the line segment connecting the base circle center O ₂ of the base circle center O ₁ and the driven scroll 4 of the drive scroll 2 as shown in FIG. 6 attached to the member 8 It is provided on the side opposite to the center O ₂ of the base circle of the driven scroll 4 on the line of action of the load F, and on the side opposite to the gas load F direction.

Also, the mounting seat 93 of the third bearing portion 93
As shown in FIG. 6, a support piece 93f, which is in contact with and supported by the driven-side support member 8 when the third bearing portion 93 is tilted, is provided on the opposite side of the swing piece 93e in b. .

As described above, the support shaft 81 is connected to the center O ₁ of the base circle of the driving scroll 2 and the driven scroll 4 as described above.
From the foregoing action line of the gas load F, so attached to the opposite side of the base circle center O ₂ of the driven scroll 4, gas to the driven scroll 4 through the midpoint of the line segment connecting the the base circle center O ₂ When the load F acts, the third bearing portion 93 swings about the support shaft 81 in the direction in which the basic circle center O ₂ approaches the basic circle center O ₁ ,
Since the spiral bodies 22 and 42 act in a direction in which they are separated from each other, in the fourth embodiment, the spiral bodies 2 are separated from each other.
As shown in FIG. 6, a spring B is attached so as to push the spiral bodies 2 and 42 so that the spiral bodies 22 and 42 can be reliably sealed by pulling the spring B, and the spiral chamber When a pressure increase such as liquid compression occurs in 63, the load due to the fluid pressure in the spiral chamber 63 overcomes the pulling force of the spring B and the gap between the spiral bodies 22, 42 is widened. It is designed to prevent compression.

Moreover, the third bearing portion 93 is attached to the driven-side support member 8 via the support shaft 81 in a cantilevered manner, and moves in the axial direction within the predetermined gap t _2. Therefore, the third bearing portion 9
3, when the driven shaft 3 is supported by a bearing, and when the operation is stopped,
Since the driven shaft 3 is straight, the third bearing portion 93 is positioned such that the entire mounting seat 93b is separated from the driven-side support member 8 by the predetermined gap t ₂ .
After that, when the driven shaft 3 tilts due to the rotational driving, the third bearing portion 93 causes the gap t to follow the tilt.
It will tilt in the range of ₂ .

The inclination at this time is defined as an initial inclination θ. The initial inclination θ is determined by the inclination of the third bearing portion 93 of the support piece 93f on the mounting seat 93b as shown in FIG. Assuming that the point of contact with the driven-side support member 8 is the support point e, as shown in FIG.
The inclination (t ₂ / d ₂ ) obtained by the length d ₂ from the center of the support shaft 81 to the center of the support shaft 81 and the predetermined gap t ₂ is the maximum inclination, and when the maximum inclination is the initial inclination θ, This initial inclination θ is set so as to satisfy the equations 1 and 9 as in the first embodiment.

As described above, in the fourth embodiment, the scroll body 2 of each of the scrolls 2 and 4 is arranged so that liquid compression can be prevented.
Since it is possible to incline the third bearing portion 93 in accordance with the inclination of the driven shaft 3 while controlling the gap between the second and second portions 42, 42, the third bearing portion 9 due to the inclination of the driven shaft 3 is inclined.
It is possible to prevent the uneven contact of No. 3 even more favorably.

In the third and fourth embodiments, the mounting seat 93b is supported by the driven side support member 8 so that the back surface of the mounting seat 93b faces the driven side support member 8. As in the fifth embodiment shown in FIG. 8, the mounting seat 93b and the support shaft 81 are attached to the drive-side support member 7.
And the driven-side support member 8 so that the surface of the mounting seat 93b on the driven scroll 4 side faces the driven-side support member 8. When the operation is stopped, the third bearing portion 9
When the driven shaft 3 is tilted by rotational driving, the swinging piece 93 on the projecting side of the support shaft 81 is formed.
e may be lifted and the third bearing portion 93 may be tilted.

In the fifth embodiment, the driven shaft 3 of the driven scroll 4 is formed in a tubular shape, and the third bearing portion 93 is used.
In addition, a shaft portion 93c to be inserted and fitted into the cylindrical driven shaft 3 is formed.

Next, a sixth embodiment will be described with reference to FIGS. 9 and 10. In the sixth embodiment, the third bearing portion 93 is used.
To the driven side support member 8 and the scrolls 2, 4
The scroll bodies 22, 42 are slidably supported in the gas load direction by the gas pressure compressed by the meshing of the scroll bodies 22, 42, and the gap between the scroll bodies 22, 42 in each scroll 2, 4 can be controlled.

Specifically, as shown in FIGS. 9 and 10, the third bearing portion 93 is provided with a tubular portion 93a for receiving the driven shaft 3 of the driven scroll 4 and the tubular portion 93a. A guide groove 82 is formed on the surface of the driven-side support member 8 facing the scroll element portion 6 so that the attachment seat 93b of the third bearing portion 93 can slide.

As shown in FIG. 9, the guide groove 82 has the center line of the groove with respect to the line connecting the center O ₁ and O ₂ of the base circles of the scrolls 2 and 4, respectively. Center O ₁ of the base circle and the center O ₂ of the base circle of the driven scroll 4
It is formed in a state in which it is tilted by a predetermined angle about the midpoint on the line segment connecting the and, and in the sixth embodiment, this predetermined angle is an anti-rotation with respect to the rotation direction x of the drive shaft 1. The angle is tilted within the range of 0 to 90 degrees.

The guide groove 82 of the sixth embodiment is inclined by a predetermined angle in the counter-rotational direction with respect to the line connecting the base circle centers O ₁ and O _{2 so} that the scrolls 22 and 4 of the scrolls 2 and 4 are inclined.
When sliding by the gas load due to the gas pressure compressed by the meshing of two, the contact points of the spiral bodies 22 and 42 slide in the direction away from each other by the gas load due to the gas pressure.

That is, since the tangential gas load Ft acting on the driven scroll 4 is a considerably large force with respect to the radial gas load Fr acting on the driven scroll 4,
The third bearing portion 93 tries to move in the direction in which the tangential gas load Ft acting on the driven scroll 4 acts, and the third bearing portion 93 moves the guide groove 82 diagonally to the lower left in FIG. Since the center circle O ₂ of the driven scroll 4 approaches the center O ₁ of the base circle of the drive scroll 2, the slide toward the lower left diagonally as described above causes the respective scrolls to slide. Two
This means that the gap between the two and 42 moves in the direction of expansion.

Furthermore, since the scrolls 22 and 42 act in a direction in which they separate from each other due to the rotational driving of the scrolls 2 and 4, in the sixth embodiment, the third bearing portion 93 and the driven-side support member. 8, that is, in the guide groove 82, a spring B for urging the third bearing portion 93 in a direction in which the scrolls 22, 42 of the scrolls 2, 4 are pressed against each other is provided. During steady operation, the elastic force of the spring B presses the scrolls 22 and 42 of the scrolls 2 and 4 against each other, and the gas that acts on the driven scroll 4 when abnormal internal pressure such as liquid compression occurs. A spring B having a spring force that displaces the third bearing portion 93 in the direction in which the spiral bodies 22 and 42 are separated from each other under the load F is disposed.

Moreover, the mounting seat 9 of the third bearing portion 93
3b is a groove width S of the guide groove 82 in the groove of the guide groove 82.
_The guide groove 82 is slidable through a predetermined gap t ₃ obtained by the difference between ₁ and the width S ₂ of the mounting seat 93b, and the depth of the guide groove 82 is smaller than the thickness d _{3 of the} mounting seat 93b. It is formed so as to be large, and within the range of the predetermined gap t ₃ , the third bearing portion 93 can be tilted while moving in the axial direction within the guide groove 82. Therefore, depending on the predetermined gap t ₃ and the thickness d _{3 of the} mounting seat 93b, the maximum inclination (t ₃ /
d ₃ ) is required.

This maximum inclination (t ₃ / d ₃ ) is set as the initial inclination θ, and the initial inclination θ is set so as to satisfy the equations 1 and 9 as in the first embodiment. Of.

As described above, in the sixth embodiment, the third
The bearing 93 is provided on the driven side support member 8 provided on the driven scroll 4 side, and the scrolls 22, 42 of the scrolls 2, 4 are provided.
Is supported so as to be slidable in accordance with a gas load F acting on the driven scroll 4 due to the fluid pressure of the spiral chamber 63 compressed by the engagement of the swirl chamber 63 and axially movable through a predetermined gap in the slide width direction, Since the pressing means for pressing the scrolls 22 and 42 of the scrolls 2 and 4 against each other is provided, the third bearing portion 93 is pressed against the driven side support member 8 in accordance with the gas load F acting on the driven scroll 4. Since it can be slid, this sliding ensures the sealing between the spiral bodies 22 and 42 by the spring force of the spring B during steady operation, and when abnormal internal pressure such as liquid compression occurs, By sliding the third bearing portion 93 by the gas load F acting on the driven scroll 4, the gap between the spiral bodies 22, 42 can be positively widened. , To reliably avoid abnormal increase in internal pressure such as liquid compression further while according to the inclination of the driven shaft 3, it is possible to tilt the said third bearing portion 93,
It is possible to favorably prevent partial contact of the third bearing portion 93 due to the inclination of the driven shaft 3.

Further, instead of the guide groove 82, a guide rail protruding toward the driven scroll 4 side is formed in the driven side support member 8, and the driven side support at the mounting seat 93b of the third bearing portion 93 is formed. A through groove that is fitted to the guide rail and slidable along the guide rail may be formed on the surface facing the member 8.

Next, another slide type embodiment similar to the sixth embodiment will be described with reference to the seventh embodiment shown in FIGS. 11 and 12. In the seventh embodiment, the sliding direction of the third bearing portion 93 is different from that of the sixth embodiment, and the sliding direction of the third bearing portion 93 is set to the respective spiral bodies 2.
The second and second bearings 93 and 92 are arranged in the guide groove 82 with a predetermined gap in a direction in which the second and second scrolls 42 and 42 act in such a manner that they are pressed against each other by the gas load F acting on the driven scroll 4. is there.

Specifically, as shown in FIGS. 11 and 12, the mounting seat 93 of the third bearing portion 93 is provided on the surface of the driven-side support member 8 facing the scroll element portion 6.
b forms a slidable guide groove 82, and the guide groove 82 is formed such that the center line of the groove is a center line O of the drive scroll 2 with respect to a line connecting the center O ₁ and O ₂ of the base circle. It is formed by inclining a predetermined angle in the range of 0 to 90 degrees in the rotation direction x of the drive shaft 1 about a midpoint on a line segment connecting ₁ and the center O ₂ of the base circle of the driven scroll 4, and mounting seat 93b of the third bearing portion 93, the groove of the guide groove 82, the groove width S ₁ of the guide groove 82, a predetermined gap t ₃ when determined by the difference between the width S ₂ of the mounting seat 93b via And the guide groove 82.
Is formed to be larger than the thickness d ₃ of the mounting seat 93b.

In the seventh embodiment, the scrolls 2 and 4 are slanted by inclining in the rotation direction x by a predetermined angle.
When sliding by the gas load F acting on the driven scroll 4 due to the gas pressure compressed by the meshing of the spiral bodies 22, 42, the spiral bodies 22, 42 can be slid in a direction in which they are pressed against each other. You can do it.

That is, since the tangential gas load Ft acting on the driven scroll 4 is considerably larger than the radial gas load Fr acting on the driven scroll 4, the third bearing portion 93 is Since the tangential gas load Ft acting on the driven scroll 4 tends to move in the direction in which it acts, the third bearing portion 93 causes the guide groove 82 to move.
In FIG. 11, the slide is performed diagonally to the lower right.
Since the center O ₂ of the basic circle of the driven scroll 4 is separated from the center O ₁ of the basic circle of the driving scroll 2,
Therefore, the spiral bodies 22 and 42 move in a direction in which the gap between them becomes narrower.

Further, within the range of the predetermined gap t ₃ , the third bearing portion 93 can be tilted while moving in the axial direction within the guide groove 82. The maximum inclination (t ₃ / d ₃ ) is obtained from the predetermined gap t ₃ and the thickness d ₃ of the mounting seat 93b.

This maximum inclination (t ₃ / d ₃ ) is set as the initial inclination θ, and the initial inclination θ is set so as to satisfy the equations 1 and 9 as in the first embodiment. Of.

As described above, in the seventh embodiment, the third
According to the gas load F acting on the driven scroll 4 on the bearing portion 93, each spiral body 2 is attached to the driven-side support member 8 in accordance with the gas load F.
2, 42 can be slid in a direction in which they are pressed against each other.
The driven shaft 3 can be surely sealed between 2 and 42.
Since the third bearing portion 93 can be tilted in accordance with the tilt of the third bearing portion 93, it is possible to favorably prevent partial contact of the third bearing portion 93 due to the tilt of the driven shaft 3.

In the case of the slide type as in the sixth and seventh embodiments, the driven shaft 3 of the driven scroll 4 is formed in a tubular shape as in the eighth embodiment shown in FIG. The cylindrical driven shaft 3 is attached to the third bearing portion 93.
You may make it form the shaft part 93c inserted in.

Further, as in the above-mentioned respective embodiments, the axial direction regulating member 5 is integrally connected to the drive scroll 2, and the space 64 formed by the drive scroll 2 and the axial direction regulating member 5 is provided. In the case of a holding structure in which the driven scroll 4 is housed,

[0089]

## EQU2 ## It is preferable to set the initial inclination θ so as to satisfy the condition of δ / D <C ₂ / L _2- (C ₁₁ + C ₁₂ ) / 2L ₁ + θ,

[0090]

When the initial inclination θ is set so as to satisfy the equation of δ / D ≧ C ₂ / L ₂ − (C ₁₁ + C ₁₂ ) / 2L ₁ , the range of the gap δ is increased. Therefore, the degree of freedom in designing the scroll element portion 6 can be increased. Also, as in the following equation,

[0091]

[Equation 11] When designing to have a relationship of δ / D <C ₂ / L ₂ − (C ₁₁ + C ₁₂ ) / 2L ₁ , the initial inclination θ can be made small. Although each of the embodiments described above has been described with respect to the scroll type compressor, the present invention can be applied to any co-rotating scroll fluid machine, and further, as the bearing, only a sliding bearing is used. It can also be applied to rolling bearings.

When the third bearing portion 93 is a rolling bearing, strong uneven contact with the inner ring portion of the bearing can be prevented, so that the life of the bearing can be prevented from being shortened.

[0093]

According to the first aspect of the present invention, even if the drive shaft 1 tilts due to the rotational drive, the third bearing portion 93 bearing-supporting the driven shaft 3 is provided in the spiral chamber 63. Since it can be preliminarily tilted in the same direction as the tilt direction of the driven shaft 3 that is tilted by the load acting on the spiral body 42 of the driven scroll 4 due to the fluid pressure, a strong one-sided contact with the third bearing portion 93 of the driven shaft 3 Therefore, the third bearing portion 93 can be prevented from being damaged, and the reliability can be improved.

According to the second aspect of the present invention, as indicated by the equation 1, by setting the inclination so as to be larger than at least the maximum inclination α ₁ at the time of the rotational drive of the drive shaft 1 represented by the equation 6, In the case where the driven shaft 3 is not a holding structure, and when the bending due to elastic deformation is small, the driven shaft 3 does not hit the third bearing portion 93 only by tilting the drive shaft 1. The contact can be reliably prevented, and the durability of the third bearing portion 93 can be improved.

According to the third aspect of the invention, in the case of the holding structure, the initial inclination θ is set so that the condition of the mathematical expression 2 is satisfied.
Since we set

[0096]

[Equation 10] When the initial inclination θ is set so as to satisfy the formula δ / D ≧ C ₂ / L ₂ − (C ₁₁ + C ₁₂ ) / 2L ₁ , the other scroll 4 or 2 end plate Since the axial gap δ between 41 or 21 and the axial regulating member 5 can be increased, the degree of freedom in designing the scrolls 2 and 4 can be increased.

According to the fourth aspect of the invention, the spiral bodies 22, 42 are pressed against each other by the third bearing portion 93 against the driven-side support member 8 in accordance with the load due to the fluid pressure in the spiral chamber 63. Since it can be swung in the direction,
Due to this swing, the scroll body 2 of each of the scrolls 2 and 4
Since the clearance between the side surfaces of the second and second shafts 42 and 42 can be controlled and the third bearing portion 93 can be tilted according to the tilt of the driven shaft 3, the third bearing due to the tilt of the driven shaft 3 can be performed. It is possible to favorably prevent uneven contact of the portion 93.

According to the fifth aspect of the invention, the third bearing portion 93 is responsive to the load due to the fluid pressure in the spiral chamber 63.
Can be slid with respect to the driven-side support member 8 in a direction in which the spiral bodies 22, 42 are pressed against each other, and this slide can control the clearance between the side surfaces of the spiral bodies 22, 42. Since the third bearing portion 93 can be tilted according to the inclination of the driven shaft 3, it is possible to favorably prevent uneven contact of the third bearing portion 93 due to the inclination of the driven shaft 3. is there.

[Brief description of drawings]

FIG. 1 is a partial cross-sectional view of a scroll compressor showing a first embodiment of a co-rotating scroll fluid machine of the present invention.

FIG. 2 is an explanatory view of a main portion of the first embodiment, showing a state of the third bearing portion as viewed in a longitudinal sectional direction.

FIG. 3 is an explanatory view of a main part of the second embodiment, showing a state in which a third bearing part is viewed from a longitudinal sectional direction.

FIG. 4 is an explanatory view of a main portion of the third embodiment, showing a state in which the third bearing portion is seen in a plan view.

5 is an explanatory view of a main part of the third embodiment, which is a cross-sectional view taken along the line AA of FIG.

FIG. 6 is an explanatory view of a main part of the fourth embodiment, showing a state where the third bearing part is seen in a plan view.

7 is an explanatory view of a main part of the fourth embodiment, which is a cross-sectional view taken along the line AA of FIG.

FIG. 8 is an explanatory view of a main portion of the fifth embodiment, showing a state of the third bearing portion as viewed in the vertical cross-sectional direction.

FIG. 9 is an explanatory view of a main part of the sixth embodiment, showing a state where the third bearing part is seen in a plan view.

10 is an explanatory view of the main part of the sixth embodiment, which is taken along the line AA in FIG.
FIG.

FIG. 11 is an explanatory view of a main portion of the seventh embodiment, showing a state where the third bearing portion is seen in a plan view.

FIG. 12 is an explanatory view of a main part of the seventh embodiment, which is taken along line A- of FIG.
A line sectional view.

FIG. 13 is an explanatory view of a main portion of the eighth embodiment, showing a state of the third bearing portion as seen in a vertical sectional direction.

FIG. 14 is an explanatory diagram showing the basic structure of a scroll element portion of a co-rotating scroll fluid machine.

FIG. 15 is a vertical cross-sectional view of a conventional co-rotating scroll fluid machine.

FIG. 16 is an explanatory view showing the action of a gas load acting on each scroll of the co-rotating scroll fluid machine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 drive shaft 2 drive scroll 21 mirror plate 22 spiral body 3 driven shaft 4 driven scroll 41 mirror plate 42 spiral body 5 axial direction regulation member 63 spiral chamber 64 space 8 driven side support member 91 first bearing portion 92 second bearing portion 93 third Bearing part

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoshitaka Shibamoto, 3-12, Chikko Shinmachi, Sakai City, Osaka Prefecture Daikin Industry Co., Ltd., Sakai Factory Co., Ltd. (72) Inventor, Hiromichi Taniwa, 3 Tsuchiko Shinmachi, Sakai City, Osaka Prefecture No. 12 Daikin Industry Co., Ltd. Sakai Works Co., Ltd.

Claims (5)

[Claims] 1. A drive scroll (2) having an end plate (21) having a scroll (22) projecting therefrom and a drive shaft (1), and a spiral scroll meshing with the scroll (22) of the drive scroll (2). A driven scroll (4) having an end plate (41) projecting a scroll (42) forming a chamber (63) and a driven shaft (3).
And a drive scroll side end of the drive shaft (1) is supported by a first bearing portion (91), and a position of the drive shaft (1) away from the drive scroll (2) is a second bearing. A co-rotating scroll fluid machine bearing-supported by a portion (92) and bearing-supported by a third bearing portion (93) for bearing-supporting the driven shaft (3) eccentrically with respect to the axis of the drive shaft (1). In the same direction as the tilt direction of the driven shaft (3) tilted by the load acting on the scroll body (42) of the driven scroll (4) due to the fluid pressure of the spiral chamber (63), the third bearing portion ( 93) A co-rotating scroll fluid machine characterized in that an initial inclination (θ) is given to 93). 2. A total clearance between the first bearing portion (91) and the drive shaft (1) is C ₁₁ , and a total clearance between the second bearing portion (92) and the drive shaft (1) is C. ₁₂ , the first bearing portion (9
The inter-bearing length between 1) and the second bearing portion (92) is L ₁ , the third
When the initial inclination of the bearing portion (93) is θ, the initial inclination (θ) is set so as to satisfy the following condition: θ> (C ₁₁ + C ₁₂ ) / 2L _1. The co-rotating scroll fluid machine described in 1. 3. An axial regulating member (5) is integrally connected to one of the driving scroll (2) and the driven scroll (4), and the one scroll (2 or 4) and the axial regulating member (5). ) And the other scroll (4 or 2) is housed in the space (64) formed by and the initial inclination of the third bearing portion (93) is θ, and the end plate (41) of the other scroll (4 or 2). Or 21) and the axial direction regulating member (5), the axial gap is δ, the end plate (41 or 21) of the other scroll (4 or 2) is D, the first bearing portion (91). ) With the drive shaft (1) as a whole clearance C ₁₁ , the second bearing portion (92) with the drive shaft (1) as a whole clearance C ₁₂ , and the third bearing portion (9).
3) the total clearance between the driven shaft (3) and the driven shaft (3) is C ₂ , and the inter-bearing length between the first bearing portion (91) and the second bearing portion (92) is L.
_{1. When} the length of the third bearing portion (93) is L ₂ , the inclination δ of the other scroll (4 or 2) with respect to the one scroll (2 or 4) and the axial direction regulating member (5). 2. The initial inclination (θ) is set so that / D satisfies the condition of δ / D <C ₂ / L ₂ − (C ₁₁ + C ₁₂ ) / 2L ₁ + θ. Co-rotating scroll fluid machine. 4. A scroll side body (22) (42) of each scroll (2) (4) is attached to a driven side support member (8) provided with a third bearing portion (93) on the driven scroll (4) side. The swirl chamber (63), which is compressed by meshing, supports the swirl body (42) of the driven scroll (4) so as to be swingable and axially movable according to the load acting on the spiral body (42) of the driven scroll (4),
Spiral body (22) in each scroll (2) (4)
The co-rotating scroll fluid machine according to any one of claims 1 to 3, further comprising pressing means for pressing the side surfaces of (42) to each other. 5. A scroll side body (22) (42) of each scroll (2) (4) is attached to a driven side support member (8) provided with a third bearing portion (93) on the driven scroll (4) side. It is slidable according to the load acting on the spiral body (42) of the driven scroll (4) by the fluid pressure of the spiral chamber (63) compressed by meshing, and axially through a predetermined gap in the slide width direction. A pressing means is provided that is movably supported and presses the side surfaces of the scrolls (22) (42) of each scroll (2) (4) against each other.
The co-rotating scroll fluid machine according to claim 3.