JPH10103259A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of parts greatly by holding the positioning of a fixed scroll by at least three circular columnlike hold tools and guiding the revolution and drive of a movable scroll. SOLUTION: Three guide pins 4 are arranged at equal intervals on a concentric circle. Three guide pin receivers 3c which receive three guide pins 4 are provided on outer periphery of a movable scroll 3. The movable scroll 3 is rotated and driven at a predetermined turn radius in the direction shown by an arrow 5 around a center O of a crank shaft. A circle 6 shows locus of the center of a movable scroll shaft at the time. Rotation torque acts in the direction shown by an arrow 7 in the movable scroll 3 in accordance with the rotation movement of the movable scroll 3. The rotation torque is received by the guide pin receivers 3c and the guide pins 4 to prevent the rotation of the movable scroll 3. Moreover, the guide pins 4 play the role of positioning and holding a fixed scroll on a support base.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly to a scroll compressor having a guide pin used for a refrigerator or the like, which guides the orbital driving of a movable scroll and positions and fixes a fixed scroll. It is.

[0002]

2. Description of the Related Art As a first example of a conventional scroll compressor, a scroll compressor disclosed in Japanese Patent Application Laid-Open No. 55-46081 will be described. FIG. 9 shows a vertical cross section of a scroll compressor disclosed in the publication. Referring to FIG. 9, a fixed scroll 2 and a movable scroll 3 are provided in a sealed casing 1. The fixed scroll 2 is provided with fixed scroll teeth 2b on the lower surface of a fixed base plate 2a. In the movable scroll 3,
The movable scroll teeth 3b are provided on the upper surface of the movable base plate 3a. The fixed scroll 2 is fixed to the support base 24 by a plurality of fixed pins 22 so as to sandwich the movable scroll 3 therebetween. A guide pin 28 is inserted through a guide pin hole 26 provided in the support base 24. The shaft end of the guide pin 28 is loosely fitted in a movable guide recess 30 formed on the lower surface of the movable base plate 3a. One end of a crankshaft 34 is pivotally supported by a shaft hole 32 provided at the center of the support base 24. Eccentric hole 3 provided in crankshaft 34
A movable scroll shaft 38 is pivotally supported by 6. The other end of the crankshaft 34 is connected to the electric motor 39. A suction pipe 40 for sucking low-temperature and low-pressure refrigerant is connected to the fixed scroll 2, and a discharge pipe 41 for sending out the compressed high-temperature and high-pressure refrigerant is connected to the upper part of the casing 1. ing.

[0003] Next, regarding the operation of the scroll compressor,
This will be further described with reference to FIGS. FIG.
10 is a plan view of the vicinity of the support 24 shown in FIG. 9 as viewed from below.

Referring to FIG. 9 and FIG.
When the power is supplied to the crankshaft 34, the crankshaft 34 is driven to rotate. With the rotation of the crankshaft 34, the center K of the movable scroll shaft 38 fitted in the eccentric hole 36 becomes the center J of the crankshaft 34.
Drive around the orbit. At the same time, the orbiting scroll 3 pivotally supported by the orbiting scroll shaft 38 is guided by the guide pin 28 which is loosely fitted into the orbiting guide recess 30 and revolves. With the orbital drive of the movable scroll 3, the refrigerant is compressed in the compression chambers 42 and 43 formed by the fixed scroll 2 and the movable scroll 3.

The manner in which the refrigerant is compressed will be described with reference to FIGS. FIGS. 11 (a) to 11 (d) show FIG.
3 shows the positional relationship between the fixed scroll and the movable scroll in a section taken along line BB of FIG. 9 and 11
Referring to (a) to (d), the crankshaft 34 is shifted from 0 ° to 9
With the rotation from 0 ° to 180 ° to 270 °, the orbiting scroll 3 revolves while keeping its attitude relatively.
By this operation, the low-temperature and low-pressure refrigerant introduced from the suction pipe 41 once enters the compression chambers 42 and 43 opened at the outer periphery, gradually reduces the volume toward the center, and flows through the discharge port 44 to the high-temperature and high-pressure refrigerant. And discharged.

[0006] By the above operation, it is possible to convert the refrigerant into a high-temperature and high-pressure refrigerant and circulate the refrigerant in a refrigeration cycle (not shown).

Next, as a second example of the conventional scroll compressor, a scroll compressor disclosed in Japanese Patent Publication No. 5-49801 will be described. FIG. 12 is a longitudinal sectional view in which a diagram of a main part of the scroll compressor disclosed in the publication and a diagram of the entire configuration are combined. Referring to FIG.
The crankshaft 3 is inserted into a shaft hole 32 provided at the center of the support base 24.
4 is pivotally supported at one end so that rotation of the crankshaft 34 is transmitted to the movable scroll shaft 38 via the Oldham coupling 46. The other configuration is the same as the configuration of the scroll compressor described in the first example, so that the same members are denoted by the same reference numerals and detailed description thereof will be omitted.

FIG. 13 shows an Oldham coupling 46 shown in FIG.
FIG. 3 is a plan view of the support base 24 viewed from below. Referring to FIG. 13, an oval Oldham coupling 46 has a pair of keys 46a protruding in opposite directions in the radial direction, and a pair of keys (or key grooves) in the long diameter direction is formed on the surface of the ring 46. ) 4
6b. A pair of keys 46a in the minor axis direction are slidably engaged with a pair of corresponding key grooves 24b formed in the inner protrusion 24a of the support base 24, while a pair of keys in the major axis direction (or The key groove) 46b is slidably engaged with a pair of corresponding key grooves (or keys) 3d provided on the lower surface of the movable base plate 3a of the movable scroll 3.

Next, the operation of the scroll compressor configured as described above will be briefly described. Crankshaft 34
The Oldham joint 46 slides in the radial direction and the major diameter direction, and the movable scroll 3 supported by the movable scroll shaft 38 revolves without rotating. By this operation, the refrigerant can be converted into a high-temperature and high-pressure refrigerant, and the refrigerant can be circulated in a refrigeration cycle (not shown).

Next, as a third example of the conventional scroll compressor, a scroll compressor disclosed in Japanese Utility Model Publication No. 63-1031 will be described. Referring to FIG.
Except for having a rotation preventing mechanism 47 for revolving the orbiting scroll 3 without rotating by rotating the crankshaft 34, the configuration is the same as that of the scroll compressor described in the first or second example, and therefore the same. The same reference numerals are given to the members, and the detailed description thereof will be omitted.

As shown in FIG. 15, the rotation preventing mechanism 47 includes a fixed ring 47c provided with a plurality of pockets 47e and 47f having the same diameter, pitch, and pitch circle in the axial direction, and a movable scroll side ring 47d. It has a fixed part 47a and a movable part 47b. The ball element 47 is formed by the edge of the pocket 47e of the fixed ring 47c and the edge of the pocket 47f of the movable scroll side ring 47d.
g.

Next, the operation will be briefly described. FIG.
16, when the movable scroll 3 is driven, for example, clockwise in FIG. 16 by rotation of the crankshaft, the center K of the movable scroll side ring 47d also has a constant radius around the center J of the fixed ring 47c. Exercise to draw a circle. At this time, a rotational force in the clockwise direction in the drawing, that is, a moment is generated in the movable scroll 3 due to a shift between the reaction force application point of the refrigerant compression force and the driving force application point. Therefore, the movable scroll 3 tends to rotate clockwise about the center K of the movable scroll side ring 47d. However, the upper nine ball elements 4 in FIG.
7g is sandwiched between the edge of the pocket 47e of the fixed ring 47c and the edge of the pocket 47f of the movable scroll side ring 47d, so that the movable scroll side ring 47d cannot rotate. The rotation of the crankshaft is stopped, and revolves around the center J of the crankshaft.

By the above operation, the refrigerant is converted into a high-temperature and high-pressure refrigerant, and the refrigerant can be circulated in a refrigeration cycle (not shown).

[0014]

However, the above-mentioned conventional scroll compressor has the following problems.

First, in the first example, as shown in FIG. 9, a plurality of fixing pins 22 are used for positioning and fixing the fixed scroll 2 to the support base 24. Also,
In order to prevent the movable scroll 3 from rotating and to revolve while maintaining the relative positional relationship with the fixed scroll 2, the support base 24 having one end loosely fitted in a movable guide recess provided in the movable base plate 3 a. A plurality of guide pins 28 inserted into the fixing pins 26 have been used.

That is, the fixed pin 22 for determining and fixing the position of the fixed scroll 2 and the guide pin 28 for determining the position of the movable scroll 3 are indispensable. For this reason, the number of parts of the scroll compressor may increase, and the production cost may increase.

Next, in the second example, as shown in FIG. 12, independently of the fixed scroll 2 being fixed to the support 24, the movable scroll 3 is prevented from rotating and the relative position of the fixed scroll 2 is fixed. Requires the Oldham coupling 46 for revolving drive while maintaining the above. For this reason, there is a problem that the number of parts of the scroll compressor increases and the production cost increases.

Further, in the third example, as shown in FIG. 14, apart from fixing the fixed scroll 2 to the support 24, the rotation of the movable scroll 3 is prevented and the relative positional relationship between the fixed scroll 2 and the fixed scroll 2 is determined. The rotation prevention mechanism 47 for revolving and driving while maintaining was required. This rotation prevention mechanism 47
As shown in FIG. 15, the fixed part 47a and the movable part 47b
And a plurality of ball elements 47g sandwiched between them, the number of parts is larger than in the first and second examples, and the processing thereof requires time. Therefore, there is a problem that the number of parts of the scroll compressor is greatly increased, and the production cost is significantly increased.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and can perform positioning and holding of a fixed scroll on a support table and guidance of revolving drive of a movable scroll without increasing the number of parts. It is an object of the present invention to obtain a scroll compressor with reduced production costs.

[0020]

According to a first aspect of the present invention, there is provided a scroll compressor comprising a fixed scroll, a movable scroll, a support, at least three cylindrical holders, and an eccentric revolving drive. Scroll compressor. The fixed scroll has a fixed base plate and spiral fixed scroll teeth provided on one surface of the fixed base plate.
The movable scroll has a movable base plate and a spiral movable scroll tooth provided on one surface of the movable base plate and engaged with the fixed scroll teeth. The support supports the movable scroll. At least three columnar holders position and hold the fixed scroll on the support base with the movable scroll interposed therebetween. The eccentric revolving drive unit makes the movable scroll eccentrically revolve around a predetermined axis with a substantially constant turning radius. In the outer peripheral portion of the fixed base plate, there are provided cylindrical holder insertion holes for positioning and holding the fixed base plate on the support table by the respective cylindrical holders.
An outer peripheral portion of the movable base plate has an inner peripheral surface for receiving each of the columnar retainers, and a retainer guide hole for guiding the eccentric orbit of the movable scroll is provided.

According to the above arrangement, the positioning and holding of the fixed scroll and the orbital driving of the orbiting scroll are guided by at least three cylindrical holders. Therefore, the number of parts of the scroll compressor can be significantly reduced, and as a result, the production cost can be significantly reduced.

In the scroll compressor according to the second aspect of the present invention, each cylindrical holder is loosely fitted in the cylindrical holder insertion hole in the insertion direction. In that case, the fixed scroll becomes movable in the insertion direction of the columnar holder. Therefore, by pushing the fixed scroll toward the movable scroll, the degree of sealing of a closed space formed by the movable scroll can be increased, and a refrigerant having a desired pressure and temperature can be discharged. As a result, a scroll compressor having excellent compression performance can be obtained.

In the scroll compressor according to the third aspect of the present invention, the inner peripheral surface of the holder guide hole has a cross section of a radius having a length obtained by adding the radius of the cylindrical holder and a constant turning radius. At least a part of the cylindrical surface having the same. In that case,
The orbital drive of the orbiting scroll is smoothly guided, and the orbiting scroll is movable in the insertion direction of the cylindrical holder. For this reason, particularly by pushing the movable scroll toward the fixed scroll, the degree of sealing of the closed space formed by the fixed scroll can be increased, and the refrigerant having a desired pressure and temperature can be discharged. As a result, a scroll compressor having excellent compression performance can be obtained.

[0024]

BEST MODE FOR CARRYING OUT THE INVENTION

First Embodiment A scroll compressor according to a first embodiment will be described with reference to the drawings. FIG. 1 is a vertical sectional view of the scroll compressor. Referring to FIG. 1, a scroll compressor includes a fixed scroll 2 and a movable scroll 3 in a closed casing 1.
And The fixed scroll 2 includes a fixed base plate 2
The guide pin 4 is positioned and held on the support base 24 by a guide pin 4 inserted into a guide pin insertion hole 2c provided near the outer periphery of a. The movable scroll 3 is a fixed scroll 2
It is held on the support 24 so as to be sandwiched between the support 24 and the support 24. In the vicinity of the outer periphery of the orbiting scroll 3, a guide pin receiver 3c for guiding the revolving drive by the guide pin 4 is provided. Since the other configuration is the same as that of the scroll compressor described in the section of the related art, the same members are denoted by the same reference numerals,
The detailed description is omitted.

Next, the operation of the scroll compressor will be described while describing the structure of the orbiting scroll 3 in more detail. FIG. 2 is a plan view of the movable scroll 3 held on the support 24 shown in FIG. 1 as viewed from above. Referring to FIG. 2, three guide pins 4 are arranged on the same circle at equal intervals. Three guide pin receivers 3c for receiving the three guide pins 4 are provided on the outer periphery of the movable scroll 3.
Is provided. The orbiting scroll 3 is driven to revolve around a shaft center O of a crankshaft (not shown) in a direction shown by an arrow 5 with a predetermined turning radius. The circle 6 indicates the locus of the center of the movable scroll shaft (not shown) at that time. With the orbital drive of the orbiting scroll 3, a rotational torque acts on the orbiting scroll 3 in a direction indicated by an arrow 7. The rotation torque is received by the guide pin receiver 3c and the guide pin 4, and the movable scroll 3 is prevented from rotating.

FIG. 2 shows the conditions for preventing the rotation.
And FIG. 3 will be described in more detail. FIG. 3 is an enlarged plan view of the vicinity of the center of the orbiting scroll shown in FIG. First, in order to specify the revolving drive of the movable scroll, as shown in FIG. 3, an angle α between a straight line connecting the center O of the crankshaft and the center B of the movable scroll with an appropriate coordinate axis having the center O of the crankshaft as an origin. Is the crank angle. 2 and 3 show a case where the crank angle is 30 °. At the movable scroll shaft center B, the driving force of the electric motor acting in the tangential direction of the locus circle 6 is defined as Fm. A component parallel to the driving force Fm acting on the midpoint A between the crankshaft center O and the center B of the movable scroll shaft among the gas forces of the refrigerant compressed by the fixed scroll and the movable scroll is defined as a tangential gas force Fth. . The rotation preventing component for preventing the movable scroll from rotating is denoted by F, and the force exerted on the guide pin receiver 3c by the guide pin 4 is defined as a pin reaction force F.
pin.

Under the above conditions, the relationship of the torque for preventing the rotation of the orbiting scroll is Fm.OB-Fth.OA = F.R3. Here, R3 indicates the distance from the center O of the crankshaft to the center of the axis of the guide pin.

In the above equation, when the turning radius OB of the movable scroll is Ror, the following formula is obtained: Fm · Ror−Fth · 1/2 · Ror = F · R3 (1)

Of the three guide pins, the one that contributes to the rotation prevention at this crank angle is the guide pin 4
a. That is, the guide pin 4a has the guide pin receiving surface that receives the pin reaction force. At this time, the relationship between the anti-rotation component F and the pin reaction force Fpin is given by Fpin = 1 / cos θ · F (2) where θ is the angle between the two.

Further, the relationship between the radius R2 of the guide pin receiver 3c and the radius R1 of the guide pin 4 and the like is as follows: R2 = R1 + Ror (3)

The case where the crank angle is 30 ° has been described above. In addition, when the crank angle is 0 ° as shown in FIG. 4A, the guide pins involved in the rotation prevention are the guide pins 4a and 4b, and FIGS.
As shown in (d), the crank angles are 90 °, 180 °,
In the case of 270 °, the guide pins 4a, 4c, and 4b are involved in preventing rotation. In any case, there is a guide pin receiving surface that receives a pin reaction force. There is always a guide pin receiver that receives this pin reaction force regardless of the crank angle, and by satisfying the above-mentioned expressions (1) to (3), the orbiting scroll can be driven to revolve without rotating.

By the way, at least three guide pin receivers are required to receive the pin reaction force regardless of the crank angle. The reason will be described for the case of two guide pins. FIGS. 5 (a) to 5 (d)
FIG. 5 is a plan view showing a positional relationship between a guide pin and a movable scroll with respect to crank angles of 0 °, 90 °, 180 °, and 270 °, and is completely the same as the configuration shown in FIG. 4 except that the number of guide pins is two. Is the same. Referring to FIG. 5A, when the crank angle is 0 °, the guide pin 4a receives the guide pin receiver that receives the pin reaction force. At this time, the anti-rotation component F becomes equal to the pin reaction force Fpin. However, when the crank angle is 90 ° as shown in FIG.
There are no guide pin receivers a and 4b that receive the pin reaction force. Therefore, there is a state in which the rotation of the movable scroll cannot be prevented. Next, when the crank angle shown in FIG.
There is a guide pin receiver that receives the pin reaction force of b, but when the crank angle shown in FIG. 5D is 270 °, there is no guide pin receiver that receives the pin reaction force of the guide pin again. . Therefore, in a series of orbital driving of the orbiting scroll, there is a state where the rotation of the orbiting scroll itself cannot be prevented, and there is a possibility that the stable operating characteristics of the scroll compressor cannot be maintained. Therefore, at least three guide pins are required to prevent the movable scroll from rotating.

FIGS. 6A to 6D show the positional relationship between the movable scroll and the guide pin at each crank angle when there are four guide pins. In any case, there is a guide pin receiving surface that receives a pin reaction force, but since a plurality of guide pins receive torque, the pin load per guide pin becomes smaller.

The orbiting scroll is favorably revolved by the guide pin and the guide pin receiver described above. By this revolution drive, the refrigerant is converted into a high-temperature and high-pressure refrigerant by the compression chambers 42 and 43 shown in FIG. In addition, the guide pins 24 also serve to position and hold the fixed scroll 2 on the support base 24. In other words, the positioning and holding of the fixed scroll 2, the rotation prevention of the movable scroll 3, and the revolving drive guide are performed by the guide pins 4. Therefore, the number of parts of the scroll compressor can be significantly reduced, and as a result, the production cost can be reduced.

In the above description, the case where the guide pins are provided at equal intervals on the same circle has been described, but the same effect can be obtained even at irregular intervals.

Embodiment 2 As described above, in the scroll compressor, the refrigerant is compressed by the compression chamber formed by the fixed scroll and the movable scroll. Whether or not the refrigerant is properly compressed largely depends on the tightness of the compression chamber. The high-pressure refrigerant trapped in the compression chamber tends to separate the fixed scroll and the movable scroll from each other due to the pressure. For this reason, the seal between the scroll teeth and the base plate may be broken, and appropriate compression may not be performed. In order to prevent this, there is a scroll compressor in which the pressure of the refrigerant being compressed is used to increase the hermeticity between the fixed scroll and the movable scroll.

Therefore, a first example of such a scroll compressor will be described with reference to the drawings. FIG. 7 is a vertical sectional view of a main part of the scroll compressor. Referring to FIG. 7, this type of scroll compressor includes an intermediate pressure chamber 12 into which a part of the refrigerant flows through a through hole 11 provided on the fixed scroll side of the compression chamber 42. The intermediate pressure chamber 12 is sealed by a seal member 10 provided on the fixed scroll 2 and the isolation member 8. The fixed scroll 2 has a guide pin 4
Thus, it is positioned and held on the support base 24 so as to be movable in the insertion direction. That is, the guide pin insertion hole 2c provided in the fixed scroll 2 and the guide pin insertion hole 2c
The guide pin 4 inserted in the fixed scroll 2 has a function of guiding the fixed scroll 2 in the vertical direction. The other configuration is the same as the configuration of the scroll compressor shown in FIG. 1 of the first embodiment, and therefore, the same members are denoted by the same reference numerals and detailed description thereof will be omitted.

Next, the operation will be briefly described. Referring to FIG. 7, the low-temperature low-pressure refrigerant introduced into the compression chamber is, for example, as described in FIG.
Due to the orbital drive of the orbiting scroll 3, the pressure increases as the compression chamber moves near the center. The high temperature and high pressure refrigerant flows to the discharge pipe 41 via the discharge port 44 and the check valve 9.
At this time, a part of the refrigerant in the compression chamber 42 flows into the intermediate pressure chamber 12 through the through hole 11. Since the fixed scroll 2 forming a part of the wall of the intermediate pressure chamber 12 is movable in the crankshaft direction,
The fixed scroll 2 is pushed downward by the flowing refrigerant. Thus, the fixed scroll 2 and the movable scroll 3
And the airtightness of the compression chambers 42 and 43 is improved. As a result, it is possible to discharge a refrigerant having a desired pressure.

Embodiment 3 A second example of a scroll compressor in which the adhesion between a fixed scroll and a movable scroll is improved will be described with reference to the drawings.

In the second embodiment, the fixed scroll is configured to be movable in the guide pin insertion direction. In the present embodiment, the movable scroll is configured to be movable in the guide pin insertion direction. That is, referring to FIG. 8, the scroll compressor includes an intermediate pressure chamber 12 into which a part of the refrigerant flows through a through hole 11 provided on the movable scroll 3 side of the compression chamber 42. Intermediate pressure chamber 12
Is sealed by a seal member 10 provided on the movable scroll 3 and the support base 24. The diameter of the guide pin receiver 3 c provided on the movable scroll 3 is larger than the diameter of the guide pin 4. Therefore, the movable scroll 3 is movable not only in the revolution driving surface but also in the guide pin insertion direction. Therefore, the guide pin receiver 3c and the guide pin 4 have a guide function in the crankshaft direction in addition to the guide of the orbital drive of the movable scroll.

The remaining structure is the same as that of the scroll compressor shown in FIG. 1 of the first embodiment, and therefore, the same members are denoted by the same reference numerals and detailed description thereof will be omitted.

Next, the operation will be briefly described. The operation is basically the same as that of the second embodiment. Compression chamber 4
A part of the refrigerant in 2 flows through the through hole 11 to the intermediate pressure chamber 12. Since the movable scroll 3 forming a part of the wall of the intermediate pressure chamber 12 is movable in the guide pin insertion direction, the movable scroll 3 is pushed upward by the flowing refrigerant. Thereby, the adhesion between the fixed scroll 2 and the movable scroll 3 is increased, and the airtightness of the compression chambers 42 and 43 is improved. As a result, a refrigerant having a desired pressure can be discharged.

In the second and third embodiments, as described in the first embodiment, it goes without saying that the number of parts of the scroll compressor can be reduced and the production cost can be reduced.

The above-described embodiments disclosed herein are merely examples, and the scope of the present invention is defined by the appended claims, and is within the scope equivalent to the scope of the appended claims. All changes are intended to be included.

[0045]

According to the scroll compressor of the first aspect of the present invention, the positioning and holding of the fixed scroll and the revolving drive of the orbiting scroll are guided by at least three cylindrical holders. Therefore, the number of parts of the scroll compressor can be significantly reduced, and as a result, the production cost can be significantly reduced.

In the scroll compressor according to the second aspect of the present invention, since each cylindrical holder is loosely fitted in the cylindrical holder insertion hole in the insertion direction, the fixed scroll can be inserted in the cylindrical holder insertion direction. It becomes movable. Therefore, by pushing the fixed scroll toward the movable scroll, the degree of sealing of a closed space formed by the movable scroll can be increased, and a refrigerant having a desired pressure and temperature can be discharged. As a result, a scroll compressor having excellent compression performance can be obtained.

In the scroll compressor according to the third aspect of the present invention, the inner circumferential surface of the holder guide hole has a cross section having a radius having a length obtained by adding the radius of the cylindrical holder and a constant turning radius. Since it forms at least a part of the cylindrical surface of the movable scroll, the orbital drive of the movable scroll is smoothly guided, and the movable scroll is movable in the insertion direction of the cylindrical holder. For this reason, particularly by pushing the movable scroll toward the fixed scroll, the degree of sealing of the closed space formed by the fixed scroll can be increased, and the refrigerant having a desired pressure and temperature can be discharged. As a result, a scroll compressor having excellent compression performance can be obtained.

[Brief description of the drawings]

FIG. 1 is a partially broken sectional view showing a vertical section of a scroll compressor according to Embodiment 1 of the present invention.

FIG. 2 is a plan view of the movable scroll, the support base, and the guide pins shown in FIG. 1 as viewed from above.

FIG. 3 is a partially enlarged plan view of the orbiting scroll shown in FIG. 2;

4 (a) to 4 (d) show a series of orbital driving of a movable scroll, with crank angles (a) of 0 °, (b) of 90 °, (c) of 180 °, and (d). Are plan views each showing a case of 270 °.

5 (a) to 5 (d) show a series of orbital driving of a movable scroll having another shape, wherein the crank angle is (a).
10 is a plan view showing the case of 0 °, (b) is 90 °, (c) is 180 °, and (d) is a plan view of 270 °.

FIGS. 6 (a) to 6 (d) show a series of orbital driving of a movable scroll having still another shape, with crank angles (a) of 0 °, (b) of 90 °, and (c) of crank angles; 180 °,
(D) is a plan view showing a case of 270 °.

FIG. 7 is a partially cutaway sectional view showing a vertical section of a scroll compressor according to Embodiment 2 of the present invention.

FIG. 8 is a partially broken sectional view showing a vertical section of a scroll compressor according to Embodiment 3 of the present invention.

FIG. 9 is a sectional view showing a vertical section of a conventional scroll compressor.

FIG. 10 is a plan view of the support base shown in FIG. 9 as viewed from below.

11A to 11D show a series of orbital driving of a movable scroll with respect to a fixed scroll of the scroll compressor shown in FIG. 9;
°, (b) is 90 °, (c) is 180 °, (d) is 27 °
It is a top view each showing the case of 0 degree.

FIG. 12 is a sectional view showing a vertical section of another conventional scroll compressor.

FIG. 13 is a plan view of the Oldham coupling shown in FIG.

FIG. 14 is a sectional view showing a vertical section of still another conventional scroll compressor.

15 is an exploded perspective view of the rotation preventing mechanism shown in FIG.

FIG. 16 is a plan view showing the arrangement of the ring and ball elements shown in FIG.

[Explanation of symbols]

 Reference Signs List 1 casing 2 fixed scroll 2a fixed base plate 2b fixed scroll teeth 2c guide pin insertion hole 3 movable scroll 3a movable base plate 3b movable scroll teeth 3c guide pin receiver 4 guide pin

Claims (3)

[Claims] A fixed base plate (2a) and said fixed base plate (2a).
a) a fixed scroll (2) having spiral fixed scroll teeth (2b) provided on one surface of the movable base plate (3a); and a movable base plate (3a) provided on one surface of the movable base plate (3a). A movable scroll (3) having spiral movable scroll teeth (3b) engaged with the fixed scroll teeth (2b); and a support (24) for supporting the movable scroll (3).
And the support base (2) with the movable scroll (3) interposed therebetween.
4) at least three cylindrical holders (4) for positioning and holding the fixed scroll (2) thereon; and eccentric revolving of the movable scroll (3) with a substantially constant turning radius around a predetermined axis. Eccentric revolution drive unit (34, 3
8), wherein the fixed base plate (2a) is fixed to the support base (2) by the cylindrical holders (4) on the outer peripheral portion of the fixed base plate (2a).
4) A cylindrical holder insertion hole (2) for positioning and holding
c) is provided, and the outer peripheral portion of the movable base plate (3a) has an inner peripheral surface for receiving each of the columnar holders (4) to hold the movable scroll (3) for guiding the eccentric orbit. Scroll compressor provided with a tool guide hole (3c). 2. Each of the columnar holders (4) is loosely fitted in the insertion direction of the columnar holder insertion hole (2c).
The scroll compressor according to claim 1. 3. The inner peripheral surface of the holder guide hole (3c) has a cross section having a radius equal to the radius of the cylindrical holder (4) and the substantially constant turning radius. The scroll compressor according to claim 1, wherein the scroll compressor forms at least a part of a cylindrical surface.