JPH07158567A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To regulate the relative revolving angle without increasing the diameter of a bush, by providing a rotation range regulating surface between a driving projection and a driving force receiving hole, in a compressor in which a variable scroll member is revolution operated without making an autorotation. CONSTITUTION:In a driving projection 6A formed integrally to the end of a rotary shaft 6 in a scroll type compressor, rotation range regulating projection lines 6b are aligned and formed on the periphery of the projection 6A at the same intervals in the peripheral direction. A bush 10 on which a balance weight 9 is formed integrally is fitted and held to the driving projection 6A. To the bush 6, a movable scroll member is held rotatable through a bearing. The bush 10 has a driving force receiving hole 10A rotation range regulating grooves 10b are formed on the inner surface, to which the driving projection 6A is fitted, and in this case, the width between both side surface of the rotation range regulating projection lines 6b is made smaller than the width of the rotation range regulating grooves 10b, so as to allow the relative revolution of the driving projection 6A in the driving force receiving hole 10A.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a movable scroll member, which is arranged to face a fixed scroll member, and is rotatably supported on a bush eccentrically arranged at the end of a rotary shaft. A scroll-type compressor that forms a sealed space whose volume decreases based on the revolution of the movable scroll member between the spiral wall of the movable scroll member and the spiral wall of the fixed scroll member that revolve non-rotatably with the rotation of the shaft. Is.

[0002]

2. Description of the Related Art The closed space is converged between the inner end portions of the spiral walls of the fixed scroll member and the movable scroll member, and the compressed refrigerant gas in the closed space is transparently provided on the scroll substrate of the fixed scroll member. It is discharged from the discharge port. The spiral walls of the fixed scroll member and the movable scroll member are in contact with each other at a plurality of points, but it is necessary to compensate for the contact failure due to the shape error of this contact portion.

Therefore, in Japanese Patent Publication No. 58-19875, a cylindrical driving projection for transmitting the driving force is provided at a specific eccentric position at the end of the rotary shaft, and a groove for receiving the driving force is formed in the bush. And a drive projection is fitted in the groove. The drive projection fitted into the groove and the bush can rotate relative to each other, and the bush tends to rotate relative to the drive projection due to the compression reaction force received via the movable scroll member. This relative rotation direction is a direction in which the spiral wall of the movable scroll member is pressed against the spiral wall of the fixed scroll member by setting the specific eccentric position of the drive projection with respect to the end of the rotary shaft. That is, when the movable scroll member is revolving, the compression reaction force acts on the bush so that the spiral wall of the fixed scroll member and the spiral wall of the movable scroll member come into contact with each other, and even if there is some shape error in the spiral wall. The spiral walls are surely brought into contact with each other.

When the bush rotates indefinitely around the drive projection, the movable scroll member swings around the drive projection every time the compressor is turned on and off, which causes an inconvenience of interfering with surrounding parts. Therefore, in this conventional example, the rotation restricting pin is provided so as to project at the end of the rotating shaft, the arcuate rotation restricting groove is provided on the bush side, and the rotation restricting pin is inserted in the rotation restricting groove. . The arc center of the rotation restricting groove is on the central axis of the drive projection, and the bush restricts the rotation range around the drive projection to the angular range of the rotation restricting groove.

[0005]

The drive load of the compressor is large, and the drive projections and bushes are required to have strength to withstand this load. Therefore, the diameter of the drive protrusion cannot be made much smaller than the diameter of the bush. The diameter of the groove on the bush side corresponds to the diameter of the drive protrusion, and the diameter of the groove cannot be made too small compared to the diameter of the bush. It is not preferable to add an arcuate rotation restriction groove to the bush having such a limitation in terms of securing the strength of the bush. If the diameter of the bush is increased, it is possible to ensure the strength, but increasing the diameter of the bush leads to an increase in the size of the entire compressor.

An object of the present invention is to regulate the relative rotation angle between the drive protrusion and the bush without increasing the diameter of the bush.

[0007]

To this end, according to the first aspect of the present invention, a drive projection is provided at an eccentric position at the end of the rotary shaft, and the drive projection is fitted in the bush so as to be relatively rotatable. A driving force receiving hole is provided for matching, and a turning range limiting surface is provided on the outer wall surface of the driving projection and on the inner wall surface of the driving force receiving hole to limit the relative turning between them in a specific range. , The distance between the relative rotation center axis of the drive protrusion and the center axis of the rotating shaft, the distance between the center axis of the bush and the center axis of the rotating shaft, and the distance between the relative rotation center axis of the driving protrusion and the center axis of the bush. And is orthogonal to the first line connecting the central axis of the bush and the central axis of the rotating shaft, and is driven to the opposite side of the central axis of the rotating shaft with respect to the second line passing through the central axis of the bush. Set the relative rotation center axis of the protrusion, and Set the relative rotation center axis of the drive projection in the rotational direction of the rotary shaft Te.

According to a second aspect of the present invention, a driving force transmission hole is provided at an eccentric position at the end of the rotary shaft, and the bush has a passive projection for fitting in the driving force transmission hole so as to be relatively rotatable. And a rotation range restricting surface that restricts relative rotation between the inner wall surface of the driving force transmission hole and the outer wall surface of the passive protrusion within a specific range. The distance between the dynamic central axis and the central axis of the rotating shaft is made larger than the distance between the central axis of the bush and the central axis of the rotating shaft and the distance between the relative rotational central axis of the driving force transmitting hole and the central axis of the bush. Of the drive force transmitting hole on the side opposite to the central axis of the rotating shaft with respect to the second line passing through the central axis of the bush and orthogonal to the first line connecting the central axis of the bush and the central axis of the rotating shaft. The relative rotation center axis is set, and the first
The relative rotation center axis line of the driving force transmission hole is set on the rotation direction side of the rotation shaft with respect to the line.

[0009]

According to the invention described in claim 1, the rotational driving force of the rotary shaft is transmitted to the bush through the drive projection and the drive force receiving hole, and the bush revolves around the central axis of the rotary shaft. The movable scroll member revolves around the bush without rotating, and the compression reaction force F acts on the bush via the movable scroll member. This compression reaction force F acts in the tangential direction of the revolution path of the bush toward the central axis of the bush. Letting θ be the inclination of the line passing through the relative rotation center axis of the drive projection and the bush center axis with respect to the first line passing through the center axis of the bush and the center axis of the rotating shaft, the component force F ·
sin θ cos θ serves as a force for relatively rotating the bush about the drive protrusion, and the spiral wall of the movable scroll member is pressed against the spiral wall of the fixed scroll member.

The rotation range restricting surface restricts relative rotation of the bush in a direction in which the spiral wall of the movable scroll member and the spiral wall of the fixed scroll member are separated from each other. According to the second aspect of the invention, the rotational driving force of the rotary shaft is transmitted to the bush through the driving force transmission hole and the passive protrusion, and the bush revolves around the center of the rotary shaft. The rotation range restricting surface restricts relative rotation of the bush in a direction in which the spiral wall of the movable scroll member and the spiral wall of the fixed scroll member are separated from each other.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment embodying the present invention will now be described with reference to FIGS.
It will be described with reference to FIG. As shown in FIG. 1, a fixed scroll member 1 made of an aluminum alloy that also serves as a housing.
A front housing 2 and a rear housing 3 made of an aluminum alloy are joined and fixed to the. Numerals 4 and 5 are seal rings for keeping the inside of the housing airtight. A rotary shaft 6 is rotatably supported in the front housing 2 via a bearing 7. 8 is a shaft seal.

A drive projection 6A is integrally formed at the end of the rotary shaft 6. As shown in FIGS. 2 and 3, the drive protrusion 6A
On the peripheral surface of the, the rotation range regulating ridges 6b are formed in an array at equal intervals in the circumferential direction. Circumferential surface of the driving protrusion 6A is a circumference around the axis line C _2, the sectional shape of the tip of each rotational range restricting protrusion 6b is a circular arc having a center on the center axis line C _2. The rotating shaft 6 rotates in the direction indicated by the arrow R in FIG.

A bush 10 is supported on the drive projection 6A, and a balance weight 9 is integrally formed on the bush 10. The bush 10 has a movable scroll member 1
1 is rotatably supported via a bearing 12 so that the fixed scroll member 1 and the fixed scroll member 1 face each other. As shown in FIGS. 1 and 3, the central axis C ₁ of the bush 10 is eccentric with respect to the central axis C ₀ of the rotating shaft 6, and the scroll substrates 1a and 11a and the scroll walls 1b and 11b of both scroll members 1 and 11 are eccentric. Form a closed space S. The movable scroll member 11 revolves along with the rotation of the rotary shaft 6, and the closed space S
Converge toward the inner end portions of the spiral walls 1b and 11b. The balance weight 9 offsets the centrifugal force caused by the revolution movement of the movable scroll member 11.

A driving force receiving hole 10A is formed in the bush 10, and a driving projection 6A is fitted in the driving force receiving hole 10A. As shown in FIGS. 2 and 3, on the inner peripheral surface of the driving force receiving hole 10A, rotation range restricting grooves 10b are arrayed at equal intervals in the circumferential direction. Circumferential surface of the driving force nest hole 10A is a circumference around the axis line C _2, the sectional shape of the bottom surface of each rotational range limiting groove 10b is a circular arc having a center on the center axis line C _2.

One side surface 6b ₁ of the rotation range regulating ridge 6b
The cross-sectional shape of the one side surface 10 of the rotation range regulating groove 10b is
It has the same shape and size as the cross-sectional shape of b ₁ , and the rotation range regulating ridge 6
The cross-sectional shape of the other side surface 6b ₂ of b is the rotation range regulating groove 1
0b has the same shape and size as the cross-sectional shape of the other side surface 10b ₂ . The width between the both side surfaces 6b ₁ and 6b _{2 of the} rotation range regulating projection 6b is set to be the both side surfaces 10b ₁ and 10b of the rotation range regulating groove 10b.
_It is smaller than the width between the _two . That is, the angular width α of the rotation range restricting protrusion 6b with respect to the center axis line C _2, are smaller than the angular width β of the rotating range limiting groove 10b with respect to the center axis line C _2. Therefore, the drive protrusion 6A can relatively rotate within the drive force receiving hole 10A. That is, bush 1
0 is rotatable relative to the drive protrusion 6A about the central axis C ₂ .

The relative rotation range of the bush 10 is restricted between the position shown by the solid line and the position shown by the chain line in FIG. The regulation position shown by the solid line is the spiral wall 1b, 11b as shown in FIG.
The regulation position, which is defined by the mutual contact, and which is indicated by the chain line, is one side surface 6b ₁ of the rotation range regulation projection 6b of the drive projection 6A.
And the side surface 1 of the rotation range regulating groove 10b of the driving force receiving hole 10A
It is defined by the abutment with 0b ₁ . That is, the side surface 6b ₁ on the side of the rotation range regulating projection 6b and the side surface 10b ₁ on the side of the rotation range regulating groove 10b are the bush 10 for the drive projection 6A.
Is a rotation range regulation surface that regulates the relative rotation range of the above to the specific range Θ shown in FIG.

As shown in FIG. 3, the relative rotation center axis C ₂ of the drive projection 6A is relative to the first straight line L ₁ passing through the center axis C ₁ of the bush 10 and the center axis C ₀ of the rotating shaft 6. And the second straight line L ₂ passing through the central axis ₁ is arranged on the side opposite to the central axis C ₀ of the rotary shaft 6. Further, the relative rotation center axis C ₂ is arranged and set on the rotation direction side of the rotation shaft 6 indicated by the arrow R with respect to the first straight line L ₁ . That is, the central axis C ₀ of the rotary shaft 6 and the drive projection 6A
Distance x between the relative rotational center axis line C ₂ of is made larger than the distance y between the relative rotational center axis line C ₂ of the central axis line C ₁ and the driving protrusion 6A of the bushing 10. Also, the distance x is the rotation axis 6
Is greater than the distance between the central axis C ₀ of the bush 10 and the central axis C ₁ of the bush 10, that is, the revolution radius r of the bush 10.

Between the scroll substrate 11a of the movable scroll member 11 and the pressure receiving wall 2a of the front housing 2, a swivel ring 13 made of an aluminum alloy and an iron plate 14 for wear prevention are interposed. A plurality of pressure receiving projections 13a and 13b are circumferentially arranged on both surfaces of the swivel ring 13. The pressure receiving protrusion 13a and the pressure receiving protrusion 13b are arranged to face each other. The pressure receiving protrusion 13a is the plate 1
4, the pressure-receiving protrusion 13b contacts the back surface of the scroll substrate 11a of the movable scroll 11. Nickel-boron plating for wear prevention is applied to the back surface of the scroll substrate 11a which is in contact with the pressure receiving projection 13b.

A plurality of pairs (three or more pairs) of pressure receiving projections 13a, 13b facing each other are rotatably supported by cylindrical rotation preventing pins 15 made of iron. The rotation prevention pins 15 are arranged at equal intervals in the circumferential direction of the swivel ring 13, and both ends of the rotation prevention pin 15 project from the tip surfaces of the pressure receiving projections 13a and 13b.

The pressure receiving wall 2a is provided with the same number of rotation preventing holes 2b as the rotation preventing pins 15 in the circumferential direction. The scroll substrate 11a has the same number of rotation preventing holes 1 as the rotation preventing pins 15.
1c are arranged in the circumferential direction. Rotation prevention holes 2b, 11
All of c are arranged at equal angular positions. A copper sleeve 1 for wear prevention is provided in the rotation preventing holes 2b and 11c.
6, 17 are fitted and fixed. Rotation prevention holes 2b, 11
In c, the end of the rotation prevention pin 15 has rotation prevention holes 2b and 11b.
It is inserted so as to be separated from the bottom surface of c.

The movable scroll member 11 revolves around the rotary shaft 6 as the rotary shaft 6 rotates, and the refrigerant gas introduced from an inlet (not shown) on the housing enters the closed space S between the scroll members 1, 11. Inflow. The closed space S decreases in volume as the movable scroll member 11 revolves, and the inner end portions 1 of the scroll walls 1b and 11b of both scrolls 1 and 11 are reduced.
It converges toward d and 11d. The refrigerant gas compressed by the volume reduction of the closed space S is applied to the scroll substrate 1a.
The discharge valve 18 is pushed out of the upper discharge port 1c and discharged into the discharge chamber 3a in the rear housing 3. The opening degree of the discharge valve 18 is regulated by the retainer 19. The compression reaction force in the closed space S that acts on the scroll substrate 11a of the movable scroll 11 is the pressure receiving projections 13a and 13b and the plate 14.
It is received by the pressure receiving wall 2a via.

As the movable scroll member 11 revolves, the rotation prevention pin 15 rolls while being sandwiched between the inner peripheral surfaces of the sleeves 16 and 17, and the orbiting ring 13 moves from the revolution center side to the revolution position side of the movable scroll 11. Is urged to. When the inner diameters of the sleeves 16 and 17 are D and the diameter of the rotation prevention pin 15 is d, (D-d) is equal to the revolution radius r of the bush 10. Therefore, D = d + r between the inner diameter D of the sleeves 16 and 17, the diameter d of the rotation prevention pin 15, and the revolution radius of the bush 10 (that is, the revolution radius of the movable scroll member 11).
Relationship is set. This relationship defines the revolution radius of the movable scroll 11 as r. Swivel ring 13
Revolves at a radius of 1/2 of the revolution radius r of the movable scroll 11.

The turning ring 13 is about to rotate. However, since the three or more rotation preventing pins 15 are in contact with the inner peripheral surface of the sleeve 16 fixedly arranged on the pressure receiving wall 2a side, the turning ring 13 does not rotate.

The rotational driving force of the rotary shaft 6 is transmitted to the bush 10 via the driving projection 6A and the driving force receiving hole 10A, and the movable scroll member 11 makes an orbital motion. When the orbiting movement of the movable scroll member 11 starts, the refrigerant gas in the closed space S is compressed. A compression reaction force acts on the movable scroll member 11, and as shown by an arrow F in FIG.
A compression reaction force F acts on the center C ₁ of 0. Bush 10
Relative to the central axis C ₁ of the drive projection 6A and the central axis C _{2 of the} drive projection 6A.
Letting θ be an angle formed by the line L ₃ connecting the line and the first straight line L ₁ , a component force f = F · sin θ cos θ indicated by an arrow f acts on the central axis C ₁ of the bush 10. This acting direction is a direction in which the bush 10 is relatively rotated about the relative rotation center axis C ₂ from the restricting position shown by the chain line to the restricting position side shown by the solid line. Therefore, as shown in FIG. 4, the scroll wall 11b of the movable scroll member 11 is pressed against the scroll wall 1b of the fixed scroll member 1, and a high degree of sealing of the sealed space S is ensured.

FIG. 5 shows the positional relationship between the spiral walls 1b and 11b when the bush 10 is arranged at the restricting position shown by the chain line in FIG. That is, when the revolution position regulation surface 6b ₁ on the revolution position regulation protrusion 6b side and the revolution position regulation surface 11b ₁ on the revolution position regulation groove 11b contact each other, the spiral walls 1b, 1
The side surfaces of 1b do not come into contact with each other, and the closed spaces S adjacent to each other at the rear end communicate with each other through the gap Q between the spiral walls 1b and 11b. Therefore, even when liquid compression is performed at the time of start-up, the liquid refrigerant escapes from the gap Q between the spiral walls 1b and 11b, causing abnormal noise due to abnormal high pressure, breakage of the spiral wall, seizure, discharge valve damage, and electromagnetic interference. The friction surface of the clutch is prevented from slipping.

The movable scroll member 11 relatively rotates about the relative rotation center axis C ₂ of the drive projection 6A, and the relative rotation range is the rotation range regulation surface 6b ₁ on the side of the driving force transmitting projection 6b. And the rotation range regulation surface 10 on the driving force receiving groove 10b side
The contact with b ₁ regulates the specific range Θ. In order to absorb the processing error and the assembly error of the movable scroll member 11 and the fixed scroll member 1, the relative rotation angle between the drive protrusion 6A and the bush 10 may be about 5 °. Further, in order to prevent the liquid compression at the time of starting, the relative rotation angle between the drive protrusion 6A and the bush 10 is 5 ° to 10 °.
It only needs to be high. Therefore, as (β-α), 10 ° to
It may be about 15 °. By thus setting the possible relative rotation angle of the bush 10 with respect to the drive protrusion 6A, it is possible to avoid unnecessary interference between the movable scroll member 11 or the balance weight 9 and other members.

The rotation range regulating surface 6b ₁ for avoiding unnecessary interference between the movable scroll member 11 or the balance weight 9 and other members is on the outer wall surface of the drive projection 6A,
The rotation range regulation surface 10b ₁ is on the inner wall surface of the driving force receiving hole 10A. That is, it is not necessary to provide a means for restricting the range of relative rotation between the drive protrusion 6A and the bush 10 at the end of the rotary shaft 6 and at another portion of the bush 10. If a new rotation half-year regulation groove is provided on the bush 10, the bush 10
It is necessary to secure the strength of the bush 10 by increasing the diameter of
The size of the compressor increases. However, in the present embodiment in which the rotation range regulating surface is provided on the outer wall surface of the drive projection and the inner wall surface of the driving force receiving hole, the strength of the bush 10 is secured as in the conventional case, and it is not necessary to increase the diameter of the bush. is there.

The present invention is, of course, not limited to the above-mentioned embodiment, but the embodiments shown in FIGS. 6 to 9 are also possible. In the embodiment of FIG. 6, the driving projection 6B has a rectangular cross-sectional shape, and the driving force receiving hole 10B has a fan-shaped cross-sectional shape. The drive protrusion 6B can relatively rotate within the drive force receiving hole 10B around the narrow side of the fan-shaped drive force receiving hole 10B. When the bush 10 is in the solid line position, the spiral wall 1
b and 11b are in contact with each other. When the bush 10 is at the chain line position, that is, the rotation range regulation surface 10b ₃ on the driving force receiving hole 10B side and the rotation range regulation surface 6b ₃ on the driving projection 6B side.
When and are in contact with each other, a gap is created between the spiral walls 1b and 11b. The relative rotation center axis line C ₂ of the drive protrusion 6B is orthogonal to the first straight line L ₁ passing through the center axis line C ₁ of the bush 10 and the center axis line C ₀ of the rotating shaft 6, and also passes through the center axis line ₁ . The second straight line L ₂ is arranged and set on the side opposite to the central axis C ₀ of the rotary shaft 6. Further, the relative rotation center axis C ₂ is arranged and set on the rotation direction side of the rotation shaft 6 indicated by the arrow R with respect to the first straight line L ₁ .

In the embodiment shown in FIG. 7, the driving projection 6C has the driving force receiving hole 1 centered on the narrow central portion of the driving force receiving hole 10C.
Relative rotation is possible within 0C. The positional relationship among the relative rotation central axis line C _{2 of the} drive projection 6C, the central axis line C ₁ of the bush 10 and the central axis line C ₀ of the rotary shaft 6 is the same as in the above-mentioned respective embodiments. When the bush 10 is in the solid line position, the spiral walls 1b and 11b are in contact with each other. When the bush 10 is at the chain line position, that is, the rotation range regulating surfaces 10b ₄₁ , 10b ₄₂ on the driving force receiving hole 10C side and the rotation range regulating surfaces 6b ₄₁ , 6b ₄₂ on the driving projection 6C side are in contact with each other. Sometimes a gap is created between the spiral walls 1b and 11b.

In the embodiment shown in FIG. 8, the driving projection 6D having an elliptical cross section can relatively rotate within the driving force receiving hole 10D having a rectangular cross section. The positional relationship among the relative rotation central axis line C _{2 of the} drive projection 6D, the central axis line C ₁ of the bush 10 and the central axis line C ₀ of the rotary shaft 6 is the same as in the above-mentioned respective embodiments. Bush 10
Is in the solid line position, the spiral walls 1b and 11b are in contact with each other. When the bush 10 is at the position indicated by the chain line, that is, the rotation range regulating surfaces 10b ₅₁ , 10 on the driving force receiving hole 10D side.
b ₅₂ and the rotation range regulating surfaces 6b ₅₁ , 6b ₅₂ on the drive projection 6D side
When and are in contact with each other, a gap is created between the spiral walls 1b and 11b.

In the embodiment shown in FIG. 9, the driving projection 6E having a rhombic cross section can relatively rotate in the driving force receiving hole 10E. The positional relationship among the relative rotation central axis line C _{2 of the} drive projection 6E, the central axis line C ₁ of the bush 10 and the central axis line C ₀ of the rotary shaft 6 is the same as in the above-mentioned respective embodiments. When the bush 10 is in the solid line position, the spiral walls 1b and 11b are in contact with each other. When the bush 10 is at the chain line position, that is, the rotation range regulating surfaces 10b ₆₁ , 10b ₆₂ on the driving force receiving hole 10E side and the rotation range regulating surfaces 6b ₆₁ , 6b ₆₂ on the driving projection 6E side are in contact with each other. Sometimes a gap is created between the spiral walls 1b and 11b.

In the present invention, as shown in FIGS. 10 and 11, an embodiment in which a driving force transmission hole 6F is provided on the rotary shaft 6 side and a passive projection 10F is provided on the bush 10 side is also possible. On the peripheral surface of the driving force transmission hole 6F, rotation range restricting grooves 6f are formed at regular intervals in the circumferential direction. Driving force transmission hole 6
Circumferential surface of the F is circumferential about the axis C _2, the sectional shape of the bottom surface of each rotational range limiting groove 6f is a circular arc having a center on the center axis line C _2. On the inner peripheral surface of the passive protrusion 10F, the rotation range restricting ridges 10f are formed in an array at equal intervals in the circumferential direction. Peripheral surface of the passive projection 10F is a circumference around the axis line C _2, the sectional shape of the bottom surface of each rotational range restricting protrusion 10f is a circular arc having a center on the center axis line C _2.

Both side surfaces 10 of the rotation range regulating projection 10f
The width between f ₁ and 6f ₂ is set on both side surfaces 6 of the rotation range restricting groove 6f.
It is made smaller than the width between f ₁ and 6f ₂ . That is, the angular width α of the rotation range restricting protrusion 10f with respect to the center axis line C _2, there was less than angular width β of the rotating range limiting groove 6f around the relative rotational center axis line C ₂ . Therefore, the passive protrusion 10F can relatively rotate within the driving force transmission hole 6F. That is, the bush 10 is rotatable relative to the driving force transmitting hole 6F about the central axis C ₂ as in the first embodiment shown in FIG. 3, and the side surface 10f on the side of the rotation range restricting ridge 10f. ₁ and the side surface 6f ₁ on the side of the rotation range regulating groove 6f indicate the range of relative rotation of the bush 10 with respect to the drive protrusion 6F.
It becomes a rotation range regulation surface that regulates within a specific range Θ shown in FIG.

As shown in FIG. 11, the central axis C ₂ of the passive protrusion 10F has a central axis C ₁ of the bush 10 rotation axis 6
With orthogonal to the first straight line L ₁ passing through the central axis C ₀ of being arranged set on the opposite side of the central axis C ₀ of the rotating shaft 6 with respect to the second straight line L ₂ passing through the central axis line C ₁ ing. Further, the relative rotation center axis C ₂ is arranged and set on the rotation direction side of the rotation shaft 6 indicated by the arrow R with respect to the first straight line L ₁ .

When the bush 10 is at the right side chain line position, that is, when the passive projection 6F is at the solid line position, the spiral walls 1b and 11b are in contact with each other. When the bush 10 is at the left chain line position, that is, when the rotation range restriction surface 6f ₁ on the driving force transmission hole 6F side and the rotation range restriction surface 10f ₁ on the passive protrusion 10F side are in contact with each other, the spiral wall 1b, 11b
There is a gap between them.

[0036]

As described above in detail, according to the present invention, since the rotation range restricting surface is interposed between the driving projection and the driving force receiving hole or between the driving force transmitting hole and the passive projection, the bush is formed. It has an excellent effect that the relative rotation angle between the drive protrusion and the bush can be regulated without increasing the diameter.

[Brief description of drawings]

FIG. 1 is a side sectional view of an entire compressor according to an embodiment of the present invention.

FIG. 2 is an exploded perspective view of a main part.

FIG. 3 is an enlarged cross-sectional view taken along the line AA of FIG.

FIG. 4 is a sectional view taken along line BB of FIG.

FIG. 5 is a vertical cross-sectional view showing a state where the spiral walls are separated from each other.

FIG. 6 is an enlarged sectional view of an essential part showing another example.

FIG. 7 is an enlarged sectional view of an essential part showing another example.

FIG. 8 is an enlarged side sectional view of an essential part showing another example.

FIG. 9 is an enlarged side sectional view of an essential part showing another example.

FIG. 10 is an enlarged side sectional view of an essential part showing another example.

11 is a cross-sectional view taken along the line CC of FIG.

[Explanation of symbols]

1 ... Fixed scroll member 1a ... Scroll substrate, 1b
... Swirl wall, 6 ... Rotary shaft, 6A to 6E ... Drive projection, 6
b ₁ , 6b ₃₁ , 6b ₃₂ , 6b ₄₁ , 6b ₄₂ , 6b ₅₁ , 6b
₅₂ ... Rotation range control surface, 10 ... Bushing, 10A to 10E
... driving force nest _{hole, 10a 1, 10b 31, 10b} 32, 10
b ₄₁ , 10b ₄₂ , 10b ₅₁ , 10b ₅₂ ... Rotation range regulation surface, 6F ... Driving force transmitting hole, 6f ₁ ... Rotation range regulation surface, 1
0F ... passive protrusion, 10f ₁ ... rotation range restricting surface 11 ... movable scroll member, 11a ... scroll base plate, 11b ...
Swirl wall.

Claims (2)

[Claims] 1. A movable scroll member arranged to face a fixed scroll member is rotatably supported on a bush eccentrically arranged at an end of a rotary shaft, and the movable scroll member is rotated with the rotation of the rotary shaft. In a scroll compressor that forms a closed space whose volume decreases based on the revolution of the movable scroll member between the spiral wall of the movable scroll member that revolves non-rotatably and the spiral wall of the fixed scroll member, the end of the rotating shaft. A driving projection is provided at an eccentric position, and the bush is provided with a driving force receiving hole for fitting the driving projection so as to be rotatable relative to each other. On the inner wall surface, there is provided a rotation range regulating surface for regulating the relative rotation between the two in a specific range, and the distance between the relative rotation center axis of the drive projection and the center axis of the rotation shaft is the center axis of the bush. With the central axis of the rotation axis Is larger than the distance between the central axis of the bush and the central axis of the relative rotation of the drive projection, and is orthogonal to the first line connecting the central axis of the bush and the central axis of the rotating shaft, and the center of the bush. The relative rotation center axis of the drive projection is set on the side opposite to the central axis of the rotary shaft with respect to the second line passing through the axis, and the relative rotation of the drive projection is further rotated on the rotary direction side of the rotary shaft with respect to the first line. A scroll type compressor with a central axis set. 2. A movable scroll member arranged so as to face the fixed scroll member is rotatably supported on a bush eccentrically arranged at the end of the rotary shaft, and with the rotation of the rotary shaft. In a scroll compressor that forms a closed space whose volume decreases based on the revolution of the movable scroll member between the spiral wall of the movable scroll member that revolves non-rotatably and the spiral wall of the fixed scroll member, the end of the rotating shaft. A driving force transmitting hole is provided at an eccentric position, and a passive protrusion for fitting in the driving force transmitting hole so as to be rotatable relative to the bush is projectingly provided on the inner wall surface of the driving force transmitting hole and the passive protrusion. A rotation range restriction surface is provided on the outer wall surface for restricting relative rotation between the two in a specific range, and the distance between the relative rotation center axis of the driving force transmission hole and the center axis of the rotation shaft is the center of the bush. Inside the axis and axis of rotation The bush is made larger than the distance from the core axis and the distance between the central axis of the driving force transmitting hole and the central axis of the bush, and is orthogonal to the first line connecting the central axis of the bush and the central axis of the rotating shaft. The relative rotation center axis of the driving force transmission hole is set on the side opposite to the center axis of the rotating shaft with respect to the second line passing through the center axis of A scroll type compressor with the center axis of the transmission hole set.