JPH10281084A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce noise with high efficiency over wide operating numbers of evolution of low and high speed by pressing and sliding the side surface of a spiral body of an oscillating scroll and the side surface of a spiral body of a fixed scroll in the operating number of revolution which is smaller than a stipulated number of revolution by the moving of a slider and making the side surfaces non-contact states when the operating number of revolution exceeds the stipulated number of revolution. SOLUTION: In the operating number of revolution which is smaller than a stipulated number of revolution, a movable weight 17 adheres to the outer peripheral surface 5d of a slider part 5a and centrifugal force applying to a slider 5 with balance weight including the movable weight 17 is smaller than centrifugal force applying to an oscillating scroll 2. Therefore, the oscillating scroll 2 is pressed in a direction that the revolution radius of the scroll 2 becomes larger and the side surface of a spiral body 2b of the oscillating scroll 2 slides, pressing on the side surface of a spiral body 1b of a fixed scroll 1. When the operating number of revolution exceeds the stipulated number of revolution, the movable weight 17 is away from the outer peripheral surface 5d of the slider part 5a and the side surface of the spiral body 2b of the oscillating scroll 2 and the side surface of the spiral body 1b of the fixed scroll 1 become non- contact state.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for a refrigerator, an air conditioner, etc.
More specifically, the present invention relates to a scroll compressor having a slider mechanism suitable for high-speed operation.

[0002]

2. Description of the Related Art A conventional scroll compressor using a slider integrally mounted with a balance weight is disclosed, for example, in Japanese Utility Model Laid-Open No. 4-49602 and Japanese Patent Laid-Open No. 7-4909.
No. 2 and the like. FIG. 9 and FIG. 10 are a longitudinal sectional view and a transverse sectional view of a main part shown in Japanese Utility Model Laid-Open No. 4-49602, and a relational diagram of forces acting during operation.
In FIG. 9, reference numeral 1 denotes a fixed scroll in which a spiral body 1b is erected on a base plate 1a, and 2 denotes an orbiting scroll in which a spiral body 2b is erected on a base plate 2a. The compression chamber 3 is formed by shifting and eccentrically combining. A cylindrical boss 2c is formed at the center of the surface of the orbiting scroll 2 on the side opposite to the spiral 2b of the base plate 2a, and the inner peripheral surface of the boss 2c is made of a sliding material such as aluminum lead alloy. A swing bearing 4 made of a bearing material used for the bearing is fixed by press fitting or the like. Reference numeral 5 denotes a slider with a balance weight, and a balance weight portion 5b is fixed to the slider portion 5a, and is integrated as a slider 5 with a balance weight. The slider 5 with a balance weight may be composed of one member, or may be integrated by fixing a plurality of members to each other. The slider portion 5a is rotatably fitted into the oscillating bearing 4 to form a sliding bearing structure between the oscillating bearing 4 and the outer peripheral surface of the slider portion 5a. The transmission of the force of the moving scroll 2 and the slider 5 with the balance weight is supported in the radial direction.
Reference numeral 6 denotes a rotary shaft for driving the orbiting scroll 2 to revolve.
An eccentric shaft portion 6a that projects eccentrically from the axis of the rotating shaft 6 is provided at its upper end. Reference numeral 6b denotes a main shaft portion which is fitted to a main bearing (not shown) which supports the rotating shaft 6 in the radial direction. A slider 5 with a balance weight is axially supported between the eccentric shaft portion 6a and the main shaft portion 6b. Main shaft 6b
A flange portion 6c having a diameter larger than the outer diameter of is formed. FIG.
As shown at 0, a slide groove 5c is formed in the slider portion 5a, and the eccentric shaft portion 6a is mounted in the slide groove 5c. And oscillating scroll 2
Occupies the position of the normal revolution radius Rc determined by the spiral bodies 1b and 2b of the scrolls 1 and 2, and a gap 5 in the longitudinal direction is provided between the slide groove 5c and the eccentric shaft 6a.
Since 0a and 50b are set, the slider 5 with the balance weight slides along the contact surface between the slide groove 5c and the eccentric shaft 6a, that is, in the longitudinal direction, in a plane perpendicular to the axis of the rotating shaft 6. This makes it possible to change the amount of eccentricity (revolution radius) of the orbiting scroll 2. The gap 50a is a gap on the anti-eccentric direction side of the orbiting scroll 2, and the gap 50b is a gap on the eccentric direction side of the orbiting scroll 2.

When the rotating shaft 6 rotates, the rotational driving torque is transmitted from the eccentric shaft portion 6a to the orbiting scroll 2 via the slider portion 5a and the oscillating bearing 4, and is prevented from rotating by an anti-rotation mechanism (not shown). Then, the orbiting scroll 2 revolves, and the volume of the compression chamber 3 formed by combining with the fixed scroll 1 is reduced.
Refrigerant gas and the like are compressed. At this time, a centrifugal force Fc acts on the orbiting scroll 2 in the direction of its eccentricity at the position of the center of gravity with the orbital movement. Note that the centrifugal force Fc of the orbiting scroll 2 described in this specification refers to the orbiting scroll 2
And the center of gravity of the orbiting scroll 2 is the center of gravity in the state where the orbiting bearing 4 is also included. On the other hand, the centrifugal force Fb is also generated at the center of gravity of the slider 5 with the balance weight due to the rotational movement. The direction of the centrifugal force Fb is the centrifugal force Fc of the orbiting scroll 2
The direction of the center of gravity of the slider 5 with the balance weight is set to a direction 180 degrees opposite to the eccentric direction of the orbiting scroll 2 so as to be in a direction 180 degrees opposite to the above. The centrifugal force Fb of the slider 5 with the balance weight is transmitted to the orbiting scroll 2 via the orbiting bearing 4, whereby the centrifugal force Fb
, That is, the weight of the slider 5 with the balance weight and the position of the center of gravity (rotational radius) of the slider 5 can be set to offset part or all of the centrifugal force Fc of the orbiting scroll.

Generally, as shown in Japanese Patent Application Laid-Open No. 7-49092, the direction of the slide groove 5c and the eccentric shaft 6a is determined by a line connecting the axis of the rotary shaft 6 and the center of the inner diameter of the oscillating bearing 4. In other words, the eccentric direction of the oscillating scroll 2 is inclined by a predetermined amount θ in a direction opposite to the rotation direction of the rotating shaft, and as a result, as shown in FIG.
Centrifugal force Fc of the slider 5 with the balance weight is offset by the centrifugal force Fb of the slider 5 with the balance weight, and the compressed gas acting on the orbiting scroll 2 is shifted by 90 degrees from the direction of the centrifugal force Fc of the orbiting scroll 2 in the anti-rotation direction of the rotary shaft 6. The slider 5 with the balance weight is pushed in the direction in which the revolution radius of the orbiting scroll 2 is increased by the component force Fg · sin θ of the tangential gas load Fg due to the above, and the spiral body 2b of the orbiting scroll 2 during normal operation.
The side surface slides while pressing against the side surface of the scroll 1b of the fixed scroll 1, and high efficiency operation without leakage of compressed gas or the like is achieved. In addition, since there is almost no influence of centrifugal force, even when variable speed operation is performed by an inverter or the like, both spiral bodies 1
The contact pressing force of b, 2b can be made stable irrespective of the number of rotations, and considering the sliding loss on the side surfaces of both spiral bodies 1b, 2b, high efficiency operation can be performed even at high speed operation. It is a very effective slider mechanism to achieve.

[0005]

In a scroll compressor as shown in FIG. 9, as described above, the centrifugal force Fb acts on the position of the center of gravity of the slider 5 with the balance weight during the rotational movement, and the centrifugal force Fb Is transmitted to the orbiting scroll 2 via the orbiting bearing, and cancels a part or all of the centrifugal force Fc of the orbiting scroll 2 acting on the center of gravity of the orbiting scroll 2 in the direction opposite to the centrifugal force Fb.

Therefore, as shown in FIG. 9, when the centrifugal force Fb acting on the center of gravity of the slider 5 with the balance weight is set so as to offset a part of the centrifugal force Fc acting on the center of gravity of the orbiting scroll 2 during normal operation. Has an orbiting scroll 2
The oscillating scroll 2 is pushed in the direction in which the orbital radius of the oscillating scroll 2 is increased by the force of Fc-Fb in the centrifugal force acting direction of the oscillating scroll 2. Of the spiral body 1b while pressing against the side surface of the spiral body 1b, and high-efficiency operation without leakage of compressed gas or the like is achieved. On the other hand, since the centrifugal force is proportional to the square of the rotation speed, the force of Fc-Fb is high. It gets bigger when driving,
In the case of high-speed operation by an inverter or the like, the side of the scroll 2b of the orbiting scroll 2 is pressed against the side of the scroll 1b of the fixed scroll 1 with a remarkably large force, and the sliding loss between the two scrolls 1b, 2b. And the noise generated by sliding, so-called sliding noise, becomes extremely large. On the other hand, in order to eliminate such a problem at the time of high-speed operation, the centrifugal force Fb acting on the center of gravity of the slider 5 with the balance weight is set so as to cancel out all the centrifugal force Fc acting on the center of gravity of the orbiting scroll 2, When the side surfaces of the two spiral bodies 1b and 2b are not in contact with each other, the amount of leakage of the refrigerant gas, which is proportional to the time required for one rotation, is smaller during high-speed operation than during low-speed operation. The ratio of the leakage loss to the net work, that is, the so-called theoretical compression work, is small and does not cause any problem. However, when the inverter is operated at a low speed, the leakage loss of the refrigerant gas and the like becomes large. However, there was a problem that the efficiency decreased when running at low speed.

In the scroll compressor having the structure disclosed in Japanese Patent Application Laid-Open No. 7-49092, the direction of the slide groove 5c and the eccentric shaft portion 6a is determined by adjusting the axis of the rotary shaft 6 and the inner diameter of the oscillating bearing 4. It is inclined by a predetermined amount θ in a direction opposite to the rotation direction of the rotating shaft with respect to a line connecting the center, that is, the eccentric direction of the orbiting scroll 2. As a result, as shown in FIG. 11, the centrifugal force Fc of the orbiting scroll 2 is offset by the centrifugal force Fb of the slider 5 with the balance weight to minimize the effect of the centrifugal force. The slider 5 with the balance weight is revolved around the orbiting scroll 2 by the component force Fg · sin θ of the tangential gas load Fg due to the compressed gas acting on the orbiting scroll 2 while being shifted from the direction by 90 degrees in the anti-rotation direction of the rotating shaft 6. When the oscillating scroll 2 is pushed in the direction in which the radius is increased, that is, when the orbiting scroll 2 is pushed in the direction in which its own orbital radius is increased, the tangential gas load Fg due to the compressed gas acting on the orbiting scroll 2 becomes extremely large. Under the operating pressure condition, the component force Fg · sin θ of the tangential gas load Fg becomes very large, so that the side surface of the scroll 2b of the orbiting scroll 2 Is pressed against the side surface of the scroll 1b of the fixed scroll 1 with a remarkably large force. When the high-speed operation is performed under such pressure conditions, the sliding loss between the scrolls 1b and 2b is very large. In addition, there is a problem that the sliding noise generated by the sliding of the two spiral bodies 1b and 2b is remarkably increased at the same time as the performance is deteriorated due to the above.

If the running scroll compressor is stopped,
Since the differential pressure between the compression chambers 3 acts on the orbiting scroll 2 to equalize the pressure in the compression chamber 3, the gap 50 on the eccentric direction side among the longitudinal gaps between the slide groove 5c and the eccentric shaft 6a.
b is narrowed and stably stopped in a relief state in which a gap is formed in the radial direction between the side surface of the scroll 2b of the orbiting scroll 2 and the side surface of the scroll 1b of the fixed scroll 1. The state where the gap 50b on the eccentric direction side is narrowed means that the position of the slider 5 with the balance weight moves in the anti-eccentric direction side of the orbiting scroll 2 as compared with the state where the orbiting scroll 2 occupies the position of the normal revolution radius Rc. It means that the rotating shaft 6
The horizontal distance between the center of the shaft and the center of the inner diameter of the orbiting bearing 4, that is, the orbital radius of the orbiting scroll 2, is smaller than the normal orbital radius Rc. On the other hand, the horizontal distance between the center of gravity of the slider 5 with the balance weight and the axis of the rotating shaft 6 existing in the anti-eccentric direction of the orbiting scroll 2, that is, the radius of rotation of the slider 5 with the balance weight is the normal orbital radius of the orbiting scroll 2. It is larger than the normal orbital radius Rs when occupying the Rc position, and the slider 5 with the balance weight is stationary in that state. Therefore, when started up from the stationary state, the centrifugal force Fb of the slider 5 with the balance weight whose radius of rotation is increasing becomes larger than the centrifugal force Fc of the orbiting scroll 2 whose radius of revolution is decreasing. There is. In this case, the slider 5 with the balance weight moves in the anti-eccentric direction side of the orbiting scroll 2 until the gap 50b on the eccentric direction becomes zero due to the difference in centrifugal force, and the orbiting scroll 2 is in the maximum relief state (both spiral bodies). (A state in which a maximum radial gap is formed between 1b and 2b), the compression action of the refrigerant gas and the like is not performed. If the compression action is not performed, no tangential gas load is generated by the compressed gas, so that no force for increasing the orbital radius of the orbiting scroll 2 is generated, and the compression action is not performed forever. When the slider 5 with the balance weight is mounted as described above, the gap 50b in the eccentric direction side is narrowed, and a gap is formed in the radial direction between the side surfaces of the scroll 2b of the orbiting scroll 2 and the scroll 1b of the fixed scroll 1. When started from the relief state, there is a problem that compression of the refrigerant gas and the like cannot be performed.
Also, in the scroll compressor immediately after assembly, the gap 50b on the eccentric side of the longitudinal gap between the slide groove 5c and the eccentric shaft 6a is narrowed, and the side surface of the scroll 2b of the orbiting scroll 2 and the fixed scroll 1 are fixed. There may be a state where a gap is formed in the radial direction between the side surfaces of the spiral body 1b, which may cause a problem such as a poor start-up at the initial start-up.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and is intended for use in a case where an inverter or the like is operated at a wide range of operating speed from low speed to high speed.
An object is to obtain a high-efficiency, low-noise scroll compressor.

Further, the present invention provides a scroll compressor in which refrigerant gas and the like are reliably compressed from the start even when the orbiting scroll is in a relief state immediately after assembly or immediately after the compression chamber is stopped. The purpose is to obtain.

[0011]

According to a first aspect of the present invention, there is provided a scroll compressor comprising a fixed scroll having a spiral projectingly formed on a base plate and a phase of the fixed scroll spiral being 180. A swirling body forming a compression chamber is formed by projecting on the base plate by eccentrically shifting and eccentrically combining, and has a swinging scroll having a swinging bearing on the anti-swirl body side of the base plate, and an eccentric shaft portion at one end. An eccentric shaft having a rotary shaft and a slider having a slide groove, wherein the slide groove is fitted to the eccentric shaft portion, and an outer peripheral surface of the slider is rotatably fitted to the swing bearing; The eccentricity of the oscillating scroll between the slide groove and the eccentric shaft portion in the slide movement direction so that the slide movement along the slide groove is enabled in a plane perpendicular to the axis of the rotation shaft with respect to the shaft portion. Direction side and anti-bias In a scroll compressor in which a gap is formed on both sides in the direction and the revolving radius of the orbiting scroll is made variable by the sliding movement, the movement of the slider causes the orbiting at a rotation speed smaller than a specified rotation speed. The scroll side surface is pressed and slid on the scroll side surface of the fixed scroll, and when the rotation speed exceeds a specified rotation speed, the scroll side surface of the orbiting scroll and the scroll side surface of the fixed scroll are not in contact with each other. It is like that.

A scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect, further comprising a slider with a balance weight formed integrally with the slider. The weight and the position of the center of gravity are set such that the centrifugal force of the slider with the balance weight acting in the direction 180 ° opposite to the centrifugal force acting direction of the orbiting scroll is larger than the centrifugal force acting on the orbiting scroll. At a rotational speed smaller than the specified rotational speed, the magnitude must be larger than the magnitude of the centrifugal force acting on the slider with balance weight minus the magnitude of the centrifugal force acting on the orbiting scroll. The magnitude of the centrifugal force acting on the slider with balance weight when the rotation speed exceeds the rotation speed Elastic body with elastic force set to move the slider with balance weight in the direction of centrifugal force acting on the orbiting scroll so that the magnitude of the centrifugal force acting on the orbiting scroll is smaller than the magnitude of the centrifugal force acting on the orbiting scroll It is provided with.

The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the second aspect, wherein the sliding groove swings in the gap between the sliding groove and the eccentric shaft portion on the swinging eccentric direction side. A flat plate having both ends supported is inserted into the scroll eccentric side end wall, and the fixed scroll is fixed in combination with the orbiting scroll so that the eccentric shaft portion is fixed to the flat plate substantially at the center of the both ends supported position. The end face of the oscillating scroll in the eccentric direction side is in line contact with the axial direction, and the flat plate is deformed to generate an elastic force for moving the slider with the balance weight in the same direction as the centrifugal force acting direction of the oscillating scroll. is there.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1 FIG. Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. 1 is a longitudinal sectional view of a main part showing the first embodiment, FIG. 2 is a cross-sectional view of a main part of FIG. 1 and a relation diagram of a force acting during low-speed operation, and FIG. 3 is a cross-sectional view of a main part of FIG. It is a relation diagram of the force which acts at the time of driving. Parts that are the same as or correspond to those of the prior art are denoted by the same reference numerals, and description thereof is omitted. The other structure of the scroll compressor is the same as that of the known scroll compressor. As shown in FIGS. 2 and 3, the sliding direction of the slider 5 with the balance weight is set in the same direction as the centrifugal force Fc direction of the orbiting scroll 2, and 17 is formed of a magnetic material having a magnetic pole strength of qm. The weight is Mm, and the centrifugal force acting on the movable weight 17 is Fm. Slider portion 5a made of magnetic material
A balance weight portion 5b made of a non-magnetic material is fixed to the slider, and is integrated as a slider 5 with a balance weight. When the orbiting scroll 2 is located at the position of the normal revolution radius Rc determined by the scrolls 1b and 2b of the scrolls 1 and 2, the axis of the rotating shaft 6 and the movable weight 17 are balanced by the magnetic attraction Fp. The center of gravity G of the slider 5 with the balance weight in a state of being in close contact with the outer peripheral surface 5d of the slider portion 5a of the slider 5 with the weight.
The horizontal distance between the two, ie, the normal rotation radius of the slider with balance weight Rs, and the center of gravity of the slider with balance weight 5 in a state where the movable weight 17 is in close contact with the inner circular wall 5e of the balance weight portion 5b of the slider with balance weight 5 The horizontal distance between the center of gravity G1 of the slider 5 with the balance weight in a state where the G2 and the movable weight 17 are in close contact with the outer peripheral surface 5d of the slider portion 5a of the slider 5 with the balance weight by the magnetic attraction Fp is ΔR,
Assuming that the weight of the slider 5 with balance weight is Ms and the weight of the orbiting scroll 2 (including the oscillating bearing 4) is Mc,
In the present embodiment, (Ms + Mm) × Rs <Mc × Rc [Equation 1] Fp> Fm [Equation 2] at a rotation speed smaller than the specified rotation speed as shown in FIG. Then, (Ms + Mm) × (Rs + ΔR) ≧ Mc × Rc [Equation 3] Fp ≦ Fm [Equation 4] The weight Ms of the slider 5 with the balance weight and its center of gravity, the weight Mm of the movable weight 17 and its center of gravity The position, the magnetic pole strength qm, and ΔR are set.

When the scroll is operated, at a rotational speed smaller than the specified rotational speed, the magnetic attraction acting between the movable weight 17 and the slider portion 5a of the slider 5 with the balance weight is smaller than the centrifugal force Fm acting on the movable weight 17. Since Fp is larger, the movable weight 17 is in close contact with the outer peripheral surface 5d of the slider portion 5a of the slider 5 with the balance weight, as shown in FIG. The turning radius is Rs. In this state, as shown in FIG. 4, the centrifugal force Fb1 acting on the slider 5 with the balance weight in a state including the movable weight 17 is smaller than the centrifugal force Fc acting on the orbiting scroll 2, so that the orbiting scroll 2
Is pushed in the direction in which the centrifugal force acts, that is, in the direction in which the orbital radius of the orbiting scroll 2 increases. Therefore, since the side surface of the scroll 2b of the orbiting scroll 2 slides while pressing against the side surface of the scroll 1b of the fixed scroll 1, leakage of refrigerant gas or the like does not occur. When the rotation speed exceeds the prescribed rotation speed, the magnetic attraction Fp acting between the movable weight 17 and the slider portion 5a of the slider 5 with the balance weight becomes smaller than the centrifugal force Fm acting on the movable weight 17,
As shown in FIG. 3, the movable weight 17 is separated from the outer peripheral surface 5d of the slider portion 5a of the slider 5 with the balance weight, and the gap 50d between the inner weight wall 5e of the balance weight portion 5b formed of a non-magnetic material is reduced to zero. The slider 5 moves in the direction of action of the centrifugal force Fm acting on the movable weight 17 itself, and the radius of rotation of the slider 5 with the balance weight including the movable weight 17 is Rs + ΔR.
In other words, the centrifugal force Fb1 acting on the slider 5 with the balance weight in the state including the movable weight 17 becomes larger than the centrifugal force Fc acting on the orbiting scroll 2 in this state according to the locus indicated by the arrow in FIG. , The side of the spiral 2b of the orbiting scroll 2 and the spiral 1 of the fixed scroll 1
(b) No contact is made with the side surface, and no sliding noise is generated. Also, since the amount of refrigerant gas leakage is smaller during high-speed operation than during low-speed operation, the ratio of leakage loss to theoretical compression work can be reduced.

Embodiment 2 Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. FIG. 5 is a longitudinal sectional view of a main part showing the second embodiment, FIG. 6 is a cross-sectional view of the main part of FIG. 5 and a relation diagram of a force applied during operation, and FIG. FIG. 8 shows a relationship between the centrifugal force Fb of the slider 5 with the balance weight and the centrifugal force of the slider 5 with the balance weight and the elastic force of the flat plate 16 at the time (Fc + Fs). FIG. 9 is a graph showing the relationship between the number of revolutions and the ratio of leakage work of refrigerant gas to the net work required for compression of refrigerant gas, that is, the so-called theoretical compression work. The description is omitted. The other structure of the scroll compressor is the same as that of the known scroll compressor. When the orbiting scroll 2 is located at the position of the normal revolution radius Rc determined by the scrolls 1b and 2b of the scrolls 1 and 2, the horizontal distance between the axis of the rotating shaft 6 and the center of gravity of the slider 5 with the balance weight, that is, Assuming that the normal rotation radius of the slider 5 with the balance weight is Rs, the weight of the slider 5 with the balance weight is Ms, and the weight of the orbiting scroll 2 (including the swing bearing 4) is Mc, in the present embodiment, Ms × Rs> Mc × Rc [Equation 5] Weight M of the slider 5 with the balance weight so that
s and the position of the center of gravity, that is, the radius of rotation Rs are set. An eccentric side end wall 51c is located on the eccentric direction side of the orbiting scroll 2 of the slide groove 5c. The end wall 51c is orthogonal to the longitudinal direction of the slide groove 5c and has a recessed step 15 formed on the outer peripheral side of the slider portion 5a. Have been. 16 is a flat plate,
It is inserted in the eccentric direction side gap 50b so that both ends are supported by the step portion 15. 61a is the eccentric shaft 6a
The end surface in the eccentric direction located on the eccentric direction side of the orbiting scroll 2 is formed in a substantially arc shape. Before the fixed scroll 1 is combined with the orbiting scroll 2, the flat plate 16 is not deformed, and the orbiting scroll 2 is located at a position where the orbital radius is larger than the position of the normal orbital radius Rc. , Fixed scroll 1 oscillating scroll 2
And fixed to the frame 7, the orbiting scroll 2 is pushed back to the position of the normal revolution radius Rc. In such a state, the flat plate 16 is substantially at the center of the both end supporting positions, that is, substantially at the step portion 15, as shown in FIG. At the center position, the eccentric shaft portion axially makes line contact with the vertex of the eccentric end surface 61a of the eccentric shaft portion, deforms in a curved manner about the contact line, and moves in the longitudinal direction of the slide groove 5c, that is, in the sliding direction of the slider 5 with the balance weight. An elastic force Fs is generated along the elastic force Fs.
s acts as a force for pushing the slider 5 with the balance weight in the direction of increasing the orbital radius of the orbiting scroll 2, that is, in the eccentric direction. Accordingly, even when the scroll compressor is stopped, the side surface of the scroll 2b of the orbiting scroll 2 is always in contact with the side surface of the scroll 1b of the fixed scroll 1 due to this elastic force, and the orbiting scroll 2 is positioned at the normal revolution radius Rc. I do. Note that a plurality of flat plates 16 may be used. The centrifugal force is proportional to the square of the rotation speed. In this scroll compressor, Fb-Fc
Therefore, the elastic force Fs generated due to the deformation of the flat plate 16 becomes Fb−Fc <Fs [Equation 6] at a rotation speed smaller than the specified rotation speed as shown in FIG. It is set so that Fb−Fc ≧ Fs [Equation 7] when the rotation speed becomes equal to or higher than the rotation speed. Fig. 8
As shown in the figure, the reference value is set with reference to the net work required for the compression of the refrigerant gas or the like, that is, the number of revolutions at which the ratio of the leakage loss of the refrigerant gas or the like to the so-called theoretical compression work is significantly reduced.

When this scroll is operated, the centrifugal force Fb acts on the position of the center of gravity of the slider 5 with the balance weight during the rotational movement, and the centrifugal force Fb is transmitted to the oscillating scroll 2 via the oscillating bearing 4. As shown in FIG. 7, when operating at a rotation speed smaller than the specified rotation speed, the elastic force for moving the slider with the balance weight in the centrifugal force acting direction of the orbiting scroll is applied to the slider with the balance weight. Since the magnitude of the centrifugal force acting on the orbiting scroll is smaller than the magnitude of the centrifugal force acting on the orbiting scroll, the side of the spiral 2b of the orbiting scroll 2 is placed on the side of the spiral 1b of the fixed scroll 1. Sliding while pressing, no leakage of refrigerant gas etc. occurs. When the rotation speed exceeds the specified rotation speed, the elastic force to move the slider with the balance weight in the direction of centrifugal force action of the orbiting scroll increases.
Since the magnitude of the centrifugal force acting on the slider with the balance weight minus the magnitude of the centrifugal force acting on the orbiting scroll is smaller than the magnitude of the centrifugal force, the orbiting scroll 2
Of the scroll 2b and the side of the scroll 1b of the fixed scroll 1 are not in contact with each other. In addition, the elastic force for moving the slider with the balance weight in the direction of the centrifugal force of the orbiting scroll subtracts the magnitude of the centrifugal force acting on the orbiting scroll from the magnitude of the centrifugal force acting on the slider with the balance weight. Significantly smaller than the force
Although the orbiting scroll 2 is in the relief state, a gap δ is formed between the deformed flat plate 16 and the end face 15a of the step portion 15 as shown in FIG. Spiral body 2 of orbiting scroll 2
The radial gap between the b side surface and the spiral body 1b side surface of the fixed scroll 1 is δ, but since the clearance δ is set within a range where the performance does not significantly decrease, there is almost no leakage of refrigerant gas and the like. Therefore, at a rotation speed exceeding the specified rotation speed, even if the side surface of the scroll 2b of the orbiting scroll 2 does not come into contact with the side surface of the scroll 1b of the fixed scroll 1, leakage of refrigerant gas and the like can be suppressed to a very small amount.

In addition, as shown in FIG. 6, since the sliding direction of the slider 5 with the balance weight is the same as the direction of the centrifugal force Fc of the orbiting scroll 2, both the spiral bodies 1b, 2b
The magnitude of the contact pressing force is the centrifugal force Fc of the orbiting scroll 2.
The tangential gas load F due to the compressed gas acting on the orbiting scroll 2 is shifted from the direction by 90 degrees in the anti-rotation direction of the rotating shaft 6.
Since the influence of g is not affected at all, the contact pressing force of both spiral bodies 1b and 2b can be made stable regardless of the operating pressure condition. This makes it very easy to set the elastic force Fs of the elastic body when setting the prescribed rotational speed.

Further, the slide groove 5c and the eccentric shaft 6a
With respect to the line connecting the axis of the rotary shaft 6 and the center of the inner diameter of the oscillating bearing 4, that is, the eccentric direction of the orbiting scroll 2.
When the rotation axis is inclined by a predetermined amount θ in the opposite direction to the rotation direction of the rotation axis, the direction of the centrifugal force Fc of the orbiting scroll 2 is shifted by 90 degrees in the anti-rotation direction of the rotation axis 6 and acts on the orbiting scroll 2. Component force Fg of tangential gas load Fg by compressed gas
Due to sin θ, the slider 5 with the balance weight is pushed in the direction in which the orbital radius of the orbiting scroll 2 is increased, that is, the force of the orbiting scroll 2 in the direction in which its orbital radius is increased is newly applied. However, in a limited operating pressure state, the side surface of the scroll 2b of the orbiting scroll 2 slides while pressing against the side surface of the scroll 1b of the fixed scroll 1 at a rotation speed smaller than the specified rotation speed. If there is no leakage of refrigerant gas or the like and the rotation speed exceeds the specified number of revolutions, the side surface of the scroll 2b of the orbiting scroll 2 does not contact the side surface of the scroll 1b of the fixed scroll 1, and no sliding noise is generated.

When the scroll compressor is stopped, a differential pressure between the compression chambers 3 acts on the orbiting scroll 2 to equalize the pressure in the compression chamber 3 and overcomes the elastic force Fs, thereby temporarily turning the orbiting scroll. 2 is formed in a relief state in which a gap is formed in the radial direction between the side surface of the spiral body 2b and the side surface of the spiral body 1b of the fixed scroll 1.
Is applied in a direction in which the orbital radius of the orbiting scroll 2 is to be increased.
Of the scroll 2b of the fixed scroll 1 comes into pressure contact with the side of the scroll 2b. That is, the orbiting scroll 2
Is always at the normal revolution radius Rc during the stop. Therefore, since the orbiting scroll 2 during stop is not stopped at a relief state, that is, at the position of the orbital radius smaller than the orbital radius Rc, the orbital radius of the orbiting scroll 2 at the time of starting is always the normal orbital radius Rc. The radius of rotation of the slider 5 with the balance weight also takes a regular value.
For this reason, the centrifugal force Fb of the slider 5 with the balance weight does not become larger than the centrifugal force Fc of the orbiting scroll 2 at the time of startup, and the relief problem of the orbiting scroll 2 related to the centrifugal force does not occur. . Therefore, the compression action of the refrigerant gas and the like is reliably performed from the moment of activation. Further, since the fixed scroll 1 is fixed to generate an elastic force as described above, the orbiting scroll 2 is always positioned at the normal revolution radius Rc after assembling. Are performed.

[0021]

As described above, the scroll compressor according to the first aspect of the present invention includes the slider, and the side of the scroll body of the orbiting scroll is rotated at a rotation speed smaller than the specified rotation speed by moving the slider. The fixed scroll is pressed and slid on the side surface of the scroll, and at a rotation speed exceeding a specified number of rotations, the side surface of the scroll of the orbiting scroll and the side surface of the scroll of the fixed scroll are not in contact with each other. At a rotation speed lower than the specified rotation speed, there is no leakage of refrigerant gas, etc. At a rotation speed higher than the specified rotation speed, no sliding noise occurs between the side surface of the scroll scroll scroll and the fixed scroll scroll surface. There is an effect that a high-efficiency and low-noise scroll compressor can be obtained over a wide range of operation speed from high to high speed.

The scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect, further comprising a slider with a balance weight integrally formed with the slider, and the weight of the slider with the balance weight and its weight. The position of the center of gravity is set to be 180 degrees smaller than the centrifugal force acting on the orbiting scroll.
The centrifugal force of the slider with the balance weight acting in the opposite direction is set to be larger, and the centrifugal force acting on the slider with the balance weight acts on the orbiting scroll at a rotation speed smaller than the specified rotation speed. The centrifugal force acting on the oscillating scroll should be greater than the magnitude of the centrifugal force subtracting the magnitude of the centrifugal force from the centrifugal force acting on the slider with the balance weight when the rotational speed exceeds the specified rotational speed. An elastic body that sets the elastic force to move the slider with the balance weight in the direction of centrifugal force action of the orbiting scroll so that it is smaller than the magnitude of the force obtained by subtracting the magnitude of At low rotational speeds, the spiral scroll side faces are pressed and slid on the fixed scroll spiral side faces, and When the rotation speed exceeds the minimum rotation speed, a small gap is formed between the spiral scroll side surface and the fixed scroll scroll side surface, and the scroll surface becomes out of contact. At a rotation speed lower than the specified rotation speed, there is no leakage of refrigerant gas and the like. When the rotation speed exceeds the rotation speed, no sliding noise occurs between the spiral scroll side surface and the fixed scroll scroll side surface, and high efficiency over a wide operating speed range from low to high speed and a wide operating pressure range Thus, there is an effect that a low noise scroll compressor can be obtained.

The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the second aspect of the present invention, wherein the gap between the slide groove and the eccentric shaft portion on the side of the oscillating scroll is eccentric. The eccentric shaft of the eccentric shaft portion is fixed to the flat plate substantially at the center of the both end supporting positions by loading a flat plate having both ends supported on the side end wall and fixing the fixed scroll in combination with the oscillating scroll. Since the eccentric side end face makes line contact in the axial direction and the flat plate is deformed, an elastic force for moving the slider with the balance weight in the same direction as the centrifugal force acting direction of the orbiting scroll is generated. In addition to the effects of the present invention, there is an effect that an elastic force can be obtained with a simple and inexpensive structure. Even if the orbiting scroll is relieved due to the differential pressure, the orbiting scroll is pushed back to the normal orbital radius by elastic force immediately after the pressure equalization, and is swung by the centrifugal force of the slider with the balance weight at startup. There is no problem that the moving scroll is relieved and the compression action of the refrigerant gas or the like cannot be performed, and a highly reliable scroll compressor that can reliably perform the compression action from the moment of startup is obtained.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a main part showing Embodiment 1 of the present invention.

FIG. 2 is a cross-sectional view of a main part of FIG. 1 and a relation diagram of forces acting during low-speed operation.

FIG. 3 is a cross-sectional view of a main part of FIG. 1 and a relation diagram of forces acting during high-speed operation.

FIG. 4 is a diagram illustrating the relationship between the force of Fb1 and the force of Fc when the rotation speed is changed according to the first embodiment of the present invention.

FIG. 5 is a vertical sectional view showing a main part of a second embodiment of the present invention.

6 is a cross-sectional view of a main part of FIG. 5 and a relation diagram of forces acting during operation.

FIG. 7 is a diagram showing the relationship between the force of Fb and the force of Fc + Fs when the rotation speed is changed according to the second embodiment of the present invention.

FIG. 8 is a diagram illustrating a relationship between the rotation speed and the ratio of leakage loss of refrigerant gas or the like to theoretical compression work according to the second embodiment.

FIG. 9 is a longitudinal sectional view of a main part of a conventional scroll compressor.

10 is a cross-sectional view of a main part in FIG. 9 and a relation diagram of forces acting during operation.

FIG. 11 is a cross-sectional view of a main part of a conventional scroll compressor different from FIG. 9 and a relation diagram of a force acting during operation.

[Explanation of symbols]

1 fixed scroll, 1a base plate, 1b spiral body, 2
Oscillating scroll, 2a base plate, 2b spiral body, 3 compression chamber, 4 oscillating bearing, 5 slider (slider with balance weight), 5c slide groove, 6 rotating shaft, 6a
Eccentric shaft part, 16 elastic bodies (flat plate), 50a Eccentric direction side gap, 50b Anti-eccentric direction side gap, 51c Eccentric direction side end wall, 61a Eccentric direction side end face.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroshi Ogawa 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Eiji Watanabe 2-3-2 Marunouchi 3-chome, Chiyoda-ku, Tokyo Inside Rishi Electric Co., Ltd. (72) Inventor Wataru Izumisawa 2-3-2 Marunouchi, Chiyoda-ku, Tokyo

Claims (3)

[Claims] 1. A fixed scroll in which a spiral body is projected from a base plate and a spiral body forming a compression chamber by combining the fixed scroll spiral body with an eccentricity by shifting the phase by 180 degrees on the base plate. Oscillating scroll protruding from the base plate and having an oscillating bearing on the side opposite to the spiral body, a rotary shaft having an eccentric shaft portion at one end, and a slider having a slide groove. The slider is fitted to the eccentric shaft portion, and the outer peripheral surface of the slider is rotatably fitted to the oscillating bearing. The slider extends along a slide groove in a plane perpendicular to the axis of the rotating shaft with respect to the eccentric shaft portion. A gap is formed between the slide groove and the eccentric shaft portion in the sliding movement direction on both the eccentric direction side and the anti-eccentric direction side of the orbiting scroll so that the sliding movement is enabled. Rocking In a scroll compressor in which the revolving radius of a crawl is variable, the side surface of the scroll of the orbiting scroll is pressed against the side surface of the scroll of the fixed scroll at a rotation speed smaller than a specified rotation speed by moving the slider. A scroll compressor characterized in that the side surface of the scroll of the orbiting scroll is not in contact with the side surface of the scroll of the fixed scroll at a rotation speed exceeding a specified rotation speed. 2. A slider having a balance weight formed integrally with the slider, wherein the weight and the position of the center of gravity of the slider with the balance weight are adjusted by the swinging scroll rather than the centrifugal force acting on the swinging scroll. The centrifugal force of the slider with the balance weight acting in the direction 180 ° opposite to the direction of the centrifugal force acting on the slider is set so as to be larger. Therefore, it is necessary to reduce the magnitude of the centrifugal force acting on the slider with the balance weight so that the magnitude becomes larger than the magnitude obtained by subtracting the magnitude of the centrifugal force acting on the orbiting scroll. It is smaller than the magnitude of the force obtained by subtracting the magnitude of the centrifugal force acting on the moving scroll. 2. The scroll compressor according to claim 1, further comprising an elastic body which sets an elastic force to move the slider with the balance weight in the direction of the centrifugal force of the orbiting scroll. 3. A fixed scroll in which a flat plate having both ends supported with respect to an end wall of an eccentric direction of the oscillating scroll of the slide groove is inserted into a gap between the sliding groove and the eccentric shaft portion on the eccentric direction of the oscillating scroll. Is fixed in combination with the orbiting scroll, so that the end surface of the eccentric shaft portion on the side of the orbiting scroll in the eccentric direction is in line contact with the flat plate substantially at the center of the support position at both ends, and the flat plate is deformed. 3. The scroll compressor according to claim 2, wherein an elastic force is generated to move the slider with balance weight in the same direction as the centrifugal force acting direction of the orbiting scroll.