JP2594717B2 - Scroll type fluid machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine used for a compressor for freezing or air conditioning, a pump blower for industrial use, and the like.

[0002]

2. Description of the Related Art FIG. 9 is a sectional side view showing a conventional general scroll type fluid machine disclosed in, for example, JP-A-64-77779, and FIG. is there. In FIG. 9, reference numeral 1 denotes a fixed scroll having a spiral body 1a as shown in FIG. Reference numeral 2 denotes an orbiting scroll having a spiral body 2a as shown in FIG. Reference numeral 3 denotes a compression chamber forming a substantially crescent shape formed by the spiral bodies 1a and 2a, 4 denotes a discharge port for discharging the fluid compressed in the compression chamber 3, and 5 denotes a tip end of the spiral bodies 1a and 2a. A seal member provided to seal the compression chamber 3 is provided, 6 is a swing scroll shaft, and 7 is a swing scroll bearing for supporting the swing scroll shaft 6.

[0003] Reference numeral 8 denotes a crankshaft which is eccentrically connected to the orbiting scroll shaft 6, and 9 denotes a balancer for compensating the balance of the eccentric oscillating motion against centrifugal force.
0 is a crank bearing, 11 is an electric motor, 12 is a crankshaft 8
An electric motor shaft 13 serving as a rotating shaft for transmitting the rotation to the housing 13 is a housing for accommodating the whole, in which the fixed scroll 1, the crank bearing 10, the electric motor 11 and the like are fixed. Reference numeral 14 denotes an Oldham ring, which is slidably engaged with the orbiting scroll 2 and the housing 13 in a direction orthogonal to each other, so as to suppress the rotation of the orbiting scroll 2.

Next, the operation will be described. Motor shaft 12
The electric motor 11 is driven with the orbiting scroll shaft 6 eccentrically held on the crankshaft 8 connected to the motor shaft 11. The orbiting scroll 2 includes an Oldham ring 1 provided for suppressing rotation.
4 allows the rocking motion without rotation. The spiral body 2a of the orbiting scroll 2 and the spiral body 1a of the fixed scroll 1 are eccentrically engaged with each other.
To form

As shown in FIG. 10, when the orbiting scroll 2 is operated in the range of 0 ° to 360 °, the compression chamber 3 formed in the peripheral portion moves toward the center of the spirally wound bodies 1a and 2a. , Whereby the fluid is compressed. At that time, a centrifugal force generated by the eccentric motion is generated in the orbiting scroll 2 in the radial direction, and a thrust force is generated in the axial direction as a reaction force of the fluid compression force. A conventional scroll compressor is disclosed, for example, in Japanese Patent Publication No. 1-35195.

[0006] The above-mentioned scroll type fluid machine is capable of achieving high efficiency and low noise compared to other systems, for example, reciprocating type and rotary type fluid machines, and is less likely to cause a mechanical failure. Is increasingly used as a compressor for industrial use or an industrial pump. In such a scroll type fluid machine, a mechanism for suppressing the rotation of the orbiting scroll 2 due to the rotation of the driving crankshaft 8, that is, an orbiting mechanism is required. As this rotation suppressing mechanism, an Oldham ring 14 is generally used as in the conventional example of FIG. 9 described above. As another rotation suppressing mechanism, a retainer having a plurality of storage holes for storing a plurality of steel balls is provided between the orbiting scroll and the housing. In addition, the above-mentioned conventional rotation suppressing mechanisms are all used in a wet type in which lubricating oil can be interposed.

[0007]

Since the conventional scroll-type fluid machine is constructed as described above, when the Oldham ring 14 is used as the rotation suppressing mechanism of the orbiting scroll 2, the lower surface of the orbiting scroll 2 is used. And the housing 13
Since the oridum ring 14 is connected in a mutually slidable manner with respect to the above, the sliding movement is basically performed, and therefore, lubricating oil is indispensable, and is used without using lubricating oil. In this case, sliding wear becomes remarkable, and in the worst case, the Oldham ring 14 may be seized and locked, and there are problems such as early wear of parts and noise.

In the case where a retainer containing a plurality of steel balls is used as the rotation suppressing mechanism, the retainer operates in the same manner as an axial ball bearing, and generates abnormal noise due to collision of the steel balls in the retainer. In addition, since the steel balls are supported by point contact, the surface pressure increases, and early wear and deformation of parts are liable to occur, which makes oil-free use difficult. Was.

[0009] Since even the invention has been shown and such order to solve the above problems, it is an object to obtain a scroll fluid machine that can be used in complete oil-free.

[0010]

A scroll type fluid machine according to the present invention is provided with a rotation suppressing mechanism for an inner diameter of an orbiting scroll side bearing provided on an orbiting scroll and supporting one end of a plurality of cams. The outer diameter of the cam having an eccentric amount substantially equal to the oscillating radius of the orbiting scroll is set to 50 μm to 100 μm.
It is smaller within the range of m .

[0011]

According to the scroll type fluid machine of the present invention, the rotation suppressing mechanism is provided on a plurality of cylindrical cams having an eccentric amount substantially equal to the oscillating radius of the oscillating scroll, and on one end of the cam. And a housing-side bearing provided in the housing and supporting the other end of the cam. The outer diameter of the cam is 50 μm to 100 μm with respect to the inner diameter of the orbiting scroll-side bearing. By making it smaller within the range, the swinging state is improved while suppressing the current consumption, the variation in the machining accuracy is absorbed, and the assembling property is improved.

[0012]

[Embodiment 1] An embodiment of the present invention will be described below with reference to the drawings. In FIGS. 1 and 2, portions substantially equivalent to those in FIG. 9 will be described using the same reference numerals. In FIG. 1, reference numeral 1 denotes a fixed scroll which also serves as a part of a housing, and has a spiral body 1a. Reference numeral 2 denotes an orbiting scroll, which has a spiral wound body 2a which meshes with the spiral wound body 1a. 3 is a compression chamber formed by the spiral bodies 1a and 2a, 4 is a discharge port of the compressed fluid, 5 is a seal member, 15 is a valve provided in the discharge port 4, and 16 is a discharge communicating with the discharge port 4. Tube. In FIG. 1 and FIG.
Is an orbiting scroll shaft, 7 is an orbiting scroll bearing, 8 is a crankshaft as a rotating shaft eccentrically connected to the orbiting scroll shaft 6, 9 is a balancer provided on the crankshaft,
Reference numeral 17 denotes a thrust bearing of the orbiting scroll shaft 6, 10, 18,
Denotes a crank bearing, and 11 denotes an electric motor that rotationally drives the crankshaft 8, and has an armature 11a. 13 is a housing.

Reference numeral 19 denotes three cams. As shown in FIG. 3, shafts 19 a and 19 b having an eccentric amount γ substantially equal to the swing radius of the orbiting scroll 2 are integrally provided, as shown in FIG. As shown, the orbiting scroll 2 and the housing 1
3 and is arranged between them. The outer diameter of the shaft 19a is D ₁
It has become. 20 of the inner diameter D ₂ for supporting the shaft 19a of the cam 19 provided on the swing scroll 2 bearing, 21 is a bearing for supporting the shaft 19b of the cam 19 provided in the housing 13. The cam 19 and the bearings 20 and 21 constitute a rotation suppressing mechanism of the orbiting scroll 2.

[0014] Next, the operation will be described. In the scroll-type fluid machine configured as described above, since the orbiting scroll 2 eccentrically mounted on the balancer 9 is driven by the rotation of the armature 11a, the orbiting scroll 2 has a rotational motion and an oscillating motion. Occur. However, the cam 19 provided between the orbiting scroll 2 and the housing 13
As a result, the rotation of the orbiting scroll 2 is suppressed, so that only the orbiting motion is restricted.

FIG . 4 shows the movement of the orbiting scroll 2 due to the interposition of a cam. In the figure, the swing scroll 2 shown by a solid line circle around the O ₁₁ is rotated, when the rotational movement to O _21, the sliding resistance of the rotating scroll bearing 7 is the swing scroll 2 shown by the solid line circle As a result, rotation occurs, and revolves around the origin 0. However, since the cam 19 whose eccentric radius γ is set to be equal to the revolution radius of the orbiting scroll 2 is interposed, the centers P ₁₁ , P ₂₁ , and P ₃₁ of the shaft 19a of the cam 19 on the orbiting scroll 2 side are provided.
Revolves around P ₁ , P ₂ and P ₃ by the driving force of the orbiting scroll 2 to P ₁₂ , P ₂₂ and P ₃₂ respectively. The center O ₁₁ of the swing scroll 2, P _11, P _21, which was suppressed by the cam 19, and P _31, while all synchronized, only revolves along a locus indicated by an arrow in the figure is performed.

FIG . 5 shows a shaft 19 inserted into a bearing 20.
current consumption varies the outer diameter D ₁ of the a as a parameter, a graph showing the results of measurement of the vibration level change. In the figure, the horizontal axis represents the outer diameter D ₁ of Hesi value of the axis 19a of the bearing 20 the inner diameter D ₂ (clearance), the solid line a represents the current consumption changes,
A dotted line b indicates a change in the vibration level. In FIG. 5, as the clearance of the shaft diameter difference D ₂ −D ₁ approaches 0, the current consumption changes in a direction to increase. The direct cause is that the position regulation of the three-point cam 19 becomes strict. Further, when the Ru thin Shisugi the other hand shaft diameter 19a, rattling occurs in the swing motion of the swing scroll 2, there is a tendency that the vibration becomes large. From the above measurement results, 50 to 10
About 0Myu, by the outer diameter D ₁ of the shaft 19a is thinner than the inner diameter D ₂ of the bearing 20, current consumption, vibrations, be balanced operation of harmony assemblability both obtained was observed.

Embodiment 2 FIG . In the first embodiment, ball bearings are used for the bearings 20 and 21 as shown in FIG. 3. However, as shown in FIG. 6, oil-impregnated bearings 20 and 21 made of a sintered metal or a tetrafluoroethylene resin or the like is used. May be used.

Embodiment 3 FIG . As shown in FIG. 7, the inner surfaces of the bushes 20a and 21a are made of a material 20 having excellent lubricity such as tetrafluoroethylene resin.
bearings 20, 2 formed by baking or bonding b, 21b
1 may be used.

[0019] The outer diameter D ₁ of the shaft 19a relative to the inner diameter D ₂ of the bearing 20 also in the embodiments 2,3, 50~100μ
It is set small. Thereby, a plurality of cams 1
In the case of using No. 9, it is possible to absorb a slight positional shift due to the lack of machining accuracy, and the assemblability is significantly improved.

Embodiment 4 FIG . Figure 8 shows another real施例of the invention, the housing 13 side of the bearing 21 for supporting the shaft 19b of the cam 19 two by using, in which arranged in two upper and lower stages as shown. According to the configuration described above, since the tilt of the shaft 19b of the cam 19 generated by the moment when the orbiting scroll 2 swings is corrected, the swinging motion is performed smoothly, and bearing loss can be reduced.

[0021]

As described above, according to the present invention, the rotation suppressing mechanism is provided for the orbiting scroll on the inner diameter of the orbiting scroll side bearing that supports one end of a plurality of cams. since it is configured to so that small camphor within the outer diameter from 50μm to 100μm the cam having a substantially equal amount of eccentricity and swinging radius, co the good swing while reducing the current consumption Ru obtained, work The positional deviation due to the lack of precision is absorbed, and further, effects such as remarkable improvement in assemblability are obtained.

[Brief description of the drawings]

FIG. 1 is a sectional side view of a scroll type fluid machine according to an embodiment of the present invention.

FIG. 2 is an exploded perspective view of the same machine.

FIG. 3 is a sectional side view of a main part of the machine.

FIG. 4 is an explanatory diagram of an operation of the machine.

FIG. 5 is a characteristic diagram based on measurement results of the same machine.

FIG. 6 is a sectional side view of a main part of a scroll type fluid machine according to another embodiment of the present invention.

FIG. 7 is a sectional side view of a main part of a scroll type fluid machine according to still another embodiment of the present invention.

FIG. 8 is a sectional side view of a main part of a scroll type fluid machine according to still another embodiment of the present invention.

FIG. 9 is a sectional side view of a conventional scroll fluid machine.

FIG. 10 is a sectional plan view showing the operation of the machine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Fixed scroll 1a Spiral winding 2 Oscillating scroll 2a Spiral winding 3 Compression chamber 4 Discharge port 6 Oscillating scroll shaft 8 Crankshaft 13 Housing 19 Cam 19a, 19b Shaft 20, 21 Bearing

Claims (1)

(57) [Claims] An orbiting scroll having a swirl body and a fixed scroll having a fluid discharge port and a fluid compression chamber formed by meshing with the swirl body and having a drive shaft eccentric from a center of rotation. A housing integrally provided below the fixed scroll, coupled to a drive shaft of the orbiting scroll, and internally provided with a driving device for driving the orbiting scroll; and the orbiting scroll and the housing. And an eccentric amount approximately equal to the swing radius of the orbiting scroll.
Several cylindrical cams and the orbiting scroll
Orbiting scroll-side bearing for supporting one end of the cam
And the other end of the cam provided on the housing.
Is composed of a housing-side bearing of approval by the swinging of the swing scroll, the scroll type fluid machine which discharges the fluid compressed in the compression chamber from the discharge port, the inner diameter of the upper KiYurado scroll-side bearing In contrast, a scroll type fluid machine wherein the outer diameter of the cam is reduced within a range of 50 μm to 100 μm .