JPH11236887A - Scroll type fluid machinery and manufacture thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the occurrence of a gap and interference between the vortex bodies of two scrolls during operation and to maintain high compression performance even when a revolving scroll and a fixed scroll are manufactured of materials different in the coefficient of thermal expansion. SOLUTION: In a scroll type fluid machinery provided with one fixed scroll 9 and the other revolving scroll 11 having vortex bodies 9b and 11b erected at the respective end plates, one scroll 9 is manufactured from a material having the coefficient (γf ) of thermal expansion and the other scroll 11 is manufactured from a material having the coefficient (γm ) higher than the coefficient (γf ). Provided the radius of a basic circle is (b), the typical size in a radial direction of an end plate is R, a typical temperature at the typical size R during operation is (t), and a difference between (γm ) and (γf ) is A, a phase deviating means is provided to engage the two vortex bodies with each other in a position further deviated to a position by a phase delay angle α (rad) calculated by α=R.t.Δ/b from a state deviating a phase by 180 deg..

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll fluid machine such as a scroll compressor used for a refrigerating device or an air conditioner, and a method of manufacturing the same.

[0002]

2. Description of the Related Art A conventional scroll compressor 1 includes, for example,
As shown in FIG. 8, a bottomed cylindrical housing 2, a scroll-type compression mechanism 4 supported by a frame 3 at an upper portion inside the housing 2, and below the scroll-type compression mechanism 4, that is, inside the housing 2. And a motor 5 disposed in the lower part of the frame 3 with a frame 3, and a rotating shaft 6 of the motor 5 is connected to a lower part of the scroll-type compression mechanism 4.

The housing 2 has a lower end and an upper end of a cylindrical portion 2a closed by a bottom portion 2b and a lid portion 2c, respectively. A suction pipe 7 is connected to the cylindrical portion 2a so as to penetrate the inside thereof. A discharge pipe 8 is connected to 2c so as to protrude inside. The scroll-type compression mechanism 4 includes a fixed scroll 9 fixed to the frame 3 and a frame 3
Orbiting scroll 11 supported so as to be able to revolve orbit through a thrust bearing 10 between the rotating scroll 11 and the fixed scroll 9
And an anti-rotation mechanism 12 such as an Oldham ring, which is provided on the outer surface of the orbiting scroll 11 and allows the orbiting scroll 11 to revolve orbit while preventing its rotation.

The fixed scroll 9 has a fixed end plate 9a.
And a spiral fixed-side spiral body 9b erected on the inner surface of the fixed-side end plate 9a; and a cylindrical peripheral wall portion 9c formed on the periphery of the fixed-side end plate 9a. A tip seal 13 is fitted on the tip end surface of the body 9b. The fixed-side end plate 9a has a discharge port 14 formed at the center thereof so as to penetrate vertically, and a discharge valve 15 for opening and closing the discharge port 14 is provided on the upper surface thereof.

At the upper end of the peripheral wall 9c, a cavity lid 16 is fixed in an airtight state, and a discharge cavity 17 is formed therein. The opening end of the discharge pipe 8 is fixed to the cavity lid 16 in a penetrating state, and the discharge pipe 8 and the discharge cavity 17 are connected. In addition, the peripheral wall 9c
A suction passage 18 communicating between the inner surface of the fixed end plate 9a and the housing 2 is formed in the suction passage 18, and the suction passage 18 is connected to a suction chamber 19 formed between the fixed scroll 9 and the orbiting scroll 11. Is done.

The orbiting scroll 11 is engaged with the orbiting end plate 11a disposed opposite to the fixed side end plate 9a and the fixed side spiral body 9b which stands on the inner surface of the orbiting end plate 11a. A spiral swirling side spiral body 11b,
A tip seal 13 is fitted on the tip end surface of the turning-side spiral body 11b. A cylindrical boss 20 is provided upright on the outer surface of the revolving side end plate 11a with the same axis, and a bush 21 is rotatably fitted inside the boss 20 via a revolving bearing 22. ing. The bush 21
Is formed with a through hole 21a eccentric from the axis.

When the fixed scroll 9 and the orbiting scroll 11 are eccentric by a predetermined distance from each other, the fixed scroll 9b and the orbiting scroll 11b are 180 ° so that the side surfaces of the fixed scroll 9b and the orbiting scroll 11b are in line contact with each other at a plurality of locations. Are engaged with each other. In this state, the tip seals 13 of the fixed-side spiral body 9b and the swirling-side spiral body 11b are in close contact with the inner surfaces of the swing-side end plate 11a and the fixed-side end plate 9a, respectively, as shown in FIG. In addition, compression chambers P, which are closed spaces, are formed at a plurality of locations having a point-symmetrical positional relationship with respect to the centers of the fixed spiral body 9b and the swirling spiral body 11b.

The rotation preventing mechanism 12 is shown in FIGS.
As shown at 0, an Oldham ring 23 is provided below the orbiting scroll 11 and on the inner peripheral surface of the frame 3 and has a predetermined diameter smaller than the inner diameter of the frame 3 by a predetermined amount. The Oldham rings 23 are 18
Two frame-side keys 23a protruding from the outer peripheral edge at a position rotated by 0 °, and these frame-side keys 23a
And two turning-side keys 23b formed at positions rotated by 90 ° with respect to each other.

The frame 3 has two frame-side keyways 3a formed on the inner peripheral surface thereof at positions rotated by 180 ° about an axis, and these frame-side keyways 3a are formed.
, The frame side key 23a is fitted so as to be movable in the radial direction. In addition, as shown in FIG.
Two turning-side key grooves 11c are formed at positions rotated by 0 °, and the turning-side key 23b is fitted so as to be movable in the radial direction. Therefore, the orbiting scroll 11 is arranged so as to be able to revolve and revolve in a state in which the orbiting scroll 11 is prevented from rotating with respect to the frame 3 via the Oldham ring 23.

The rotating shaft 6 of the motor 5 has an upper bearing 24 and a lower bearing 2 disposed on the inner peripheral surface of the frame 3.
Eccentric pin 26 which is supported by the shaft 5 and is eccentric by a predetermined amount from the axis
Are provided at the upper end in a protruding state. The eccentric pin 26
Is inserted into the through hole 21a of the bush 21 and rotatably supports the bush 21. Further, the eccentric pin 26
A balance weight 28 is fixed to a lower portion of the chamber 27 in a chamber 27 formed between the orbiting scroll 11 and the frame 3.

The eccentric pin 26 and the rotating shaft 6 include:
An oil passage 29 penetrating these up and down is formed, and a lubricating oil pump 30 is provided at the lower end of the rotary shaft 6, and is connected to the lower end of the oil passage 29. A lubricating oil 31 is stored in the bottom 2 b of the housing 2, and the lower end of the rotary shaft 6 is disposed in the lubricating oil 31. Further, the frame 3 has an oil drain hole 3b communicating the chamber 27 with the lower portion of the frame 3, and a passage 3c arranged on the outer peripheral portion of the frame 3 and communicating the upper portion and the lower portion of the frame 3.

Next, a method of compressing gas (fluid) in the conventional scroll compressor 1 will be described.

When the motor 5 is driven, the rotation of the rotary shaft 6 is transmitted to the orbiting scroll 11 via the eccentric pin 26, the bush 21, the orbit bearing 22, and the boss 20, and the orbiting scroll 11 is rotated by the rotation preventing mechanism 1.
The revolving orbiting motion is performed on the fixed scroll 9 in a state where the rotation of the fixed scroll 9 is stopped by 2. At this time, the gas is supplied from the suction pipe 7 into the housing 2 and cools the motor 5, and further, the passage 3c, the suction passage 18 and the suction chamber 1
9 and is supplied to the compression chamber P.

The gas in the compression chamber P is transferred to the central portion while being compressed as the volume of the compression chamber P is reduced by the orbital movement of the orbiting scroll 11. further,
The compressed gas is discharged into the discharge cavity 17 by opening the discharge valve 15 from the discharge port 14, and is discharged from the discharge cavity 17 to the outside by the discharge pipe 8.

The lubricating oil 31 stored in the bottom 2b
Is sucked up by the lubricating oil pump 30 and passes through the inside of the oil passage 29 from the distal end of the eccentric pin 26. The eccentric pin 26, the bush 21, the slewing bearing 22, the thrust bearing 10, the lower bearing 25, the rotation preventing mechanism 12, etc. Lubricate. Thereafter, the lubricating oil 31 is returned from the chamber 27 to the bottom 2b of the housing 2 via the oil drain hole 3b and stored.

Incidentally, the fixed scroll 9 and the orbiting scroll 11 in the conventional scroll compressor 1 may be formed of different materials depending on cost and function. For example, the fixed scroll 9 and the orbiting scroll 11 are revolved with respect to the fixed scroll 9 formed of cast iron. In some cases, the orbiting scroll 11 that performs orbiting motion is formed of an aluminum alloy that is lighter than cast iron.

[0017]

However, if the fixed scroll 9 and the orbiting scroll 11 are formed of different materials as in the above-mentioned conventional scroll compressor 1, as shown in FIG. Even when the fixed scroll 9b and the revolving scroll 11b are engaged with each other with a phase difference of 180 ° so that the side surfaces of the fixed scroll 9b and the revolving scroll 11b are in line contact with each other at a plurality of positions, the revolving scroll 11 is revolved to operate. As shown in FIG. 9A, the temperature rises due to the compression of the gas due to the swirling, and the fixed-side spiral body 9
A gap δ is generated between the rotation-side spiral body 11b and the turning-side spiral body 11b, and a phenomenon that they interfere with each other occurs. That is, due to the difference in the coefficient of thermal expansion between the materials, a difference in the shape of the two spiral bodies due to the rise in temperature causes a gap δ or interference, and the gap δ
For example, there is a problem that the compression performance of the scroll compressor is reduced due to leakage of gas from the compressor.

The present invention has been made in view of the above-mentioned problem, and even when the orbiting scroll and the fixed scroll are made of materials having different coefficients of thermal expansion, a gap or interference between the scrolls of both scrolls during operation is provided. An object of the present invention is to provide a scroll-type fluid machine that does not occur and can maintain high compression performance and a method for manufacturing the scroll-type fluid machine.

[0019]

Means for Solving the Problems The present inventors have conducted research (for example, a technique described in Japanese Patent Application Laid-Open No. 60-198301) on the generation and interference of a spiral body in a scroll type fluid machine. As a result, the following findings were obtained.

As shown in FIG. 12, the scroll type fluid machine is configured such that involute curves drawn starting from two points on the circumference of a base circle K having a radius b are formed as outer shape curves inv1 and inv2.
And a spiral body U. This spiral body U is shown in FIG.
And fixed to the end plate to form a member called a scroll.

Therefore, when the spiral body U of one scroll (hereinafter, referred to as fixed scroll) S and the spiral body U of the other scroll (hereinafter, referred to as orbiting scroll) M are engaged, the structure is as shown in FIG. You. In the drawing, ρ is the turning radius, b is the base circle radius, and φ is the turning angle (incomplete meshing).

The shape of the tip end of the spiral body U is determined by analysis in consideration of the meshing conditions and the like, for example, when the complete meshing condition is satisfied, as shown in FIG. In such a scroll, as shown in FIG. 15, while the fixed scroll S is fixed and the orbiting scroll M is shifted in phase by 180 °, the orbiting scroll M is rotated around the fixed scroll S via a rotation preventing mechanism. Is turned at a predetermined radius.

Thus, the fixed scroll S and the orbiting scroll M cooperate to form a compression chamber P, and the orbiting motion of the orbiting scroll M is changed from FIG. 16A to FIG. 16F.
, The compression chamber P moves from the peripheral part to the central part. The compression chamber P completes the confinement of the fluid in this process, and the volume gradually decreases, so that the fluid can be continuously pumped.

In the compressor, gas is compressed as a fluid by the orbiting motion of the orbiting scroll M, and the temperature rises. Therefore, in the scroll, the central part having a high degree of compression has a higher temperature than the peripheral part,
Thermal expansion corresponding to the temperature occurs. In addition, centrifugal force acts on the orbiting scroll M to perform a circular motion. Since this force causes the orbiting scroll M to vibrate, as described above, the orbiting scroll M is formed of a lightweight material such as an aluminum alloy to reduce the force.

In particular, when an iron-based material is used for the fixed scroll S and an aluminum alloy is used for the orbiting scroll M, the coefficient of thermal expansion of the aluminum alloy is about twice as large as that of iron.
Interference between the spiral bodies U occurs. This can be considered that the relative position of the spiral body U in the radial direction changes due to the difference in the coefficient of thermal expansion due to the difference in the material of the end plate.

The temperature of the working gas in the compression chamber is polytropic compressed as the volume of the compression chamber decreases after the suction cutoff, and the temperature rises. The temperature of the working gas during the compression stroke is expressed by the following equation. T = T _S (V / V _C ) ^{n -1} (n: polytropic index) The volume of the compression chamber at the time of the suction cutoff is V _C , and the temperature of the working gas at the time of the suction cutoff is the compression chamber during the T _S compression process. Is V, and the temperature of the working gas during the compression process is T.

Since the compression chamber moves periodically from the periphery to the center of the end plate, the temperature at a certain point on the end plate changes periodically. Furthermore, it is high in the center and low in the periphery. Therefore, the end plate has a temperature distribution that decreases from the center to the periphery. On the other hand, the temperature rise degree t at a point located r from the center
Is the elongation of γ · rt
Is proportional to

Since t decreases with increasing r, the relationship is inversely proportional, and in fact, it can be considered that rt = constant. Therefore, if a representative dimension R from the center of the end plate and a representative temperature t at that time are taken, it can be considered that R · t = constant.

The end plates are opposed to each other by engaging the spiral body and are in substantially similar thermal environments, so that R · t is considered to be equal to each other. Therefore, the difference between the displacements of the two spiral bodies at the position of the point R is dominant in the difference in the coefficient of thermal expansion γ. This magnitude is R · t · Δ (Δ: thermal expansion coefficient difference).

This difference in the displacement amount means that the spiral body having a large γ advances the involute start point relatively by R · t · Δ. Since the scroll scroll meshes the involute curves having the same phase with each other by shifting the phase by 180 °, as shown in FIG. 12, the thermal expansion is large compared to the case where the difference in thermal expansion is ignored. Will lead the phase by the angle α = R · t · Δ (dotted line in the figure). If the spiral body having a large thermal expansion coefficient is twisted toward the angle delay side, interference between the spiral bodies due to thermal expansion in the operating state is prevented.

That is, the present invention is a technique based on the above research results, and employs the following configuration in order to solve the above-mentioned problems. In the scroll type fluid machine according to the present invention,
Equipped with one scroll and the other scroll, each of which has a spiral body that draws an involute curve defined by a base circle with the same radius on the end plate, and can rotate while the other scroll is prevented from rotating by a rotation prevention mechanism In the scroll-type fluid machine, which is rotatable at a predetermined radius by an eccentric drive mechanism and enables relative orbiting motion between the scrolls, the other scroll and the one scroll are thermally expanded. A technique is employed in which the spiral bodies having different thicknesses from each other are engaged with each other at a position further shifted by an angle corresponding to the thickness difference from a state where the spiral bodies are shifted by 180 ° in phase. You.

In this scroll-type fluid machine, the spiral bodies are meshed with each other at a position further shifted by an angle corresponding to the difference in the thickness of the spiral bodies during thermal expansion from the state where the spiral bodies are shifted by 180 °. Even if the other scroll turns and compresses the fluid and the temperature rises and the thermal expansion occurs, it is possible to easily obtain a good meshing state of both the spirals without forming a gap between the spirals. Becomes

[0033] Further, there are provided one scroll and the other scroll in which a spiral body which draws an involute curve defined by a base circle having the same radius is erected on an end plate, respectively.
In a scroll type fluid machine in which the other scroll is rotatable in a state in which the other scroll is prevented from rotating by a rotation preventing mechanism and is rotatable at a predetermined radius by an eccentric drive mechanism, thereby enabling a relative orbiting movement between the scrolls. , said one scroll is made of a material the thermal expansion coefficient gamma _f, said other scroll is made are produced with a material of the thermal expansion coefficient gamma _f larger thermal expansion coefficient gamma _m, the radius of the base circle the b, R a radial typical dimension of the end plate, t representative temperature in the typical dimension R at the time of operation, the thermal expansion coefficient difference is the difference between the thermal expansion coefficient gamma _m and the thermal expansion coefficient gamma _f delta When the spiral bodies are shifted from each other by 180 °, the spiral bodies are shifted to a position further shifted by a phase delay angle α (rad) calculated by the following relational expression α = R · t · Δ / b. Phase shift hand to match Techniques are employed which are provided.

On the other hand, in the method of manufacturing a scroll type fluid machine according to the present invention, one scroll and the other scroll, each of which has a spiral body which draws an involute curve defined by a base circle having the same radius, are provided on the end plate. And a method of manufacturing a scroll-type fluid machine in which the other scrolls are rotatably assembled in a state where rotation of the scrolls is prevented by engaging each other's spirals, wherein the one scroll has a material having a thermal expansion coefficient γ _f in the manufacture, the other scroll is made are produced with a material of the thermal expansion coefficient gamma _f larger thermal expansion coefficient gamma _m, the radius of the base circle b, and radial typical dimension of the end plate R the representative temperature of the typical dimension R at the time of operation t, when the thermal expansion rate being the difference between the thermal expansion coefficient gamma _m and the thermal expansion coefficient gamma _f delta, the spiral body of each other, only 180 degree phase From the shifted state A technique including a positioning step of engaging with a position further shifted by a phase delay angle α (rad) calculated by the following relational expression α = R · t · Δ / b is adopted.

In this scroll type fluid machine and its manufacturing method, the respective spiral bodies are further shifted by 180 ° by the phase delay angle α calculated by the relational expression α = R · t · Δ / b from the state shifted by 180 °. Since the spirals are displaced by an angle corresponding to the dimensional change due to the difference in thermal expansion beforehand, there is no gap or interference between the two spirals even at high temperatures, and compression such as fluid leakage etc. Performance degradation can be prevented.

Further, the phase shift means is provided between the end plate of the one scroll and the end plate of the other scroll, and the both end plates are arranged in a predetermined radial direction with each other via a key and a key groove structure. An Oldham mechanism that slidably guides in the radial direction intersecting with the other direction, the other scroll key or keyway is used to connect the spiral bodies to each other.
Assuming that the phases are displaced by 0 °, they are arranged in a radial direction orthogonal to the predetermined radial direction, and the Oldham mechanism is arranged such that the intersecting radial direction is relative to the radial direction orthogonal to the predetermined radial direction. A technique in which the phase is set in a direction in which the phase is delayed by the phase delay angle α is adopted.

In this scroll type fluid machine, the Oldham mechanism is set so that the intersecting radial direction is delayed by a phase delay angle α with respect to the radial direction orthogonal to the predetermined radial direction. The other scroll is
Simply by fitting the key and the key groove to each other and attaching the key and the key groove to the Oldham mechanism, the keys and the key grooves are shifted by the phase delay angle α.

[0038] The phase shift means may shift the phase of the other scroll by 180 ° from the position at which the spiral of the other scroll meshes with the spiral of the one scroll by the phase delay angle α. A technique processed in advance may be adopted.

In this scroll type fluid machine, the spiral body of the other scroll is preliminarily machined to a position shifted by a phase delay angle α from a position where it meshes with the spiral body of one scroll while shifting the phase by 180 °. Therefore, there is no need to perform an operation of shifting the engagement positions of the spiral bodies during assembly.

In the method for manufacturing a scroll-type fluid machine, the spirals may be meshed with each other at a predetermined radial direction distance l from the axis, assuming that the spiral bodies are engaged with each other with a phase shift of 180 °. A scroll-side pin hole having a circumferential distance Dp of the opening is formed at a position distant from the scroll member. The stationary member to which the one scroll is fixed has a scroll member at a position separated from the axis by a distance 1 in the predetermined radial direction. A stationary member side pin hole having the same diameter as the side pin hole is formed. In the positioning step, the one scroll has the same axis as the stationary member, and the scroll side pin hole and the stationary member side have the same axis. A centering pin having a diameter dp is inserted into the pin hole, and one of the scrolls is positioned until the centering pin is sandwiched between the inner peripheral surfaces of the scroll side pin hole and the stationary member side pin hole. Includes a scroll rotating step of rotating about the axis, after the scroll rotating step, and a scrolling fixing step of said one scroll in this state is fixed to the stationary member withdrawing the centering pin,
A technique is adopted in which the circumferential distance Dp, the diameter dp, and the distance 1 of the opening are set so as to satisfy the following relational expression (Dp-dp) / 1 = α.

In this method of manufacturing a scroll type fluid machine, the circumferential distance of the opening (for example, the diameter in the case of a pin hole having a circular cross section) Dp, the diameter dp, and the distance l
Is set so that the relational expression (Dp−dp) / l = α is satisfied, so that the angle can be easily adjusted only by setting the dimensions of the centering pin, the scroll side pin hole, and the stationary member side pin hole. Can be positioned.

[0042]

FIG. 1 shows a first embodiment of a scroll compressor as a scroll type fluid machine according to the present invention.
This will be described with reference to FIG. In the scroll compressor according to the first embodiment, a description of the same configuration as the above-described conventional scroll compressor 1 will be omitted.

The difference between the scroll compressor of the first embodiment and the above-described conventional scroll compressor 1 is that, as shown in FIGS. 1 (a) and 1 (b), the scroll compressor is made of materials having different coefficients of thermal expansion. The fixed scroll (one scroll) 9 and the orbiting scroll (the other scroll) 11 move the fixed-side spiral body 9b and the orbiting spiral body 11b having the same shape by 180 degrees.
The phase delay angle α (ra
It is engaged with the position further shifted by d).

That is, the phase delay angle α is set as follows. The radius of the base circle K in the fixed-side spiral body 9b and the turning-side spiral body 11b that draws an involute curve is defined as b. Fixed scroll 9 is made of heat expansion coefficient of a material gamma _f, if the orbiting scroll 11 is manufactured of a material the thermal expansion coefficient gamma _f larger thermal expansion coefficient gamma _m, radial pivot end plate 11a the typical dimension R, a representative temperature in the typical dimension R at the time of operation t, when the thermal expansion rate being the difference between the thermal expansion coefficient gamma _m and the thermal expansion coefficient gamma _f was delta, the spiral body of each other, From the state where the phase is shifted by 180 °, the phase delay angle α is calculated by the following relational expression α = R · t · Δ / b.

In the scroll compressor having the above structure, the phase delay calculated by the relational expression α = R · t · Δ / b from the state where the fixed-side spiral body 9b and the orbiting-side spiral body 11b are shifted in phase by 180 °. When the orbiting scroll 11b is not orbiting, as shown in FIG. 1B, a gap is formed between the fixed-side spiral body 9b and the orbiting-side spiral body 11b. However, as shown in FIG. 1A, the orbiting scroll 11b
Does not change the dimensions due to the difference in thermal expansion, and no gap δ is formed between the two spiral bodies. That is, since the fixed-side spiral body 9b and the revolving-side spiral body 11b are previously displaced from each other by an angle corresponding to the dimensional change due to the difference in thermal expansion, no gap δ is generated between the two spiral bodies, and gas leaks and the compression performance is reduced. Can be prevented from decreasing.

Next, a method of positioning the fixed scroll 9 and the orbiting scroll 11 in the first embodiment will be described.

First, as shown in FIG. 11, the orbiting scroll 11 is in a state in which rotation is prevented, as in the conventional example, as shown in FIG.
The turning-side spiral body 11b is disposed with reference to a predetermined radial direction Y. A turning-side keyway 11c formed in a direction orthogonal to the predetermined radial direction Y is provided on the turning side of the Oldham ring 23 shown in FIG. The Oldham ring 2
3 attached.

The fixed-side spiral body 9b and the revolving-side spiral body 1
1b and the fixed scroll 9 are shifted in phase by 180 °. As shown in FIG. 2, the fixed scroll 9 is positioned at a position 1 away from the axis of the fixed side end plate 9a in a predetermined radial direction Y by a distance l. A scroll-side pin hole 9d having a diameter (the circumferential distance of the opening) Dp is formed. Further, the frame (stationary member) 3 to which the fixed scroll 9 is fixed has a frame-side pin hole (stationary member) having the same diameter as the scroll-side pin hole 9d at a position separated from the axis by a distance 1 in a predetermined radial direction Y. A side pin hole 3d is formed. in this way,
The fixed scroll 9b of the fixed scroll 9 is machined on the basis of the scroll pin hole 9d, and the revolving scroll 11b of the revolving scroll 11 is machined on the basis of the revolving keyway 11c.

[Scroll Rotation Step] Fixed scroll 9
2, the centering pin 40 having a diameter dp is inserted into the scroll-side pin hole 9d and the frame-side pin hole 3d as shown in FIG. At this time, the diameters dp and Dp and the distance 1 are set so as to satisfy the following relational expression (Dp-dp) / l = α. Then, as shown in FIG. 2, the fixed scroll 9 is rotated about the axis until the centering pin 40 is sandwiched between the inner peripheral surfaces of the scroll side pin hole 9d and the frame side pin hole 3d.

[Scroll Fixing Step] In this state, the fixed scroll 9 is fixed to the frame 3 and then the centering pin 40 is pulled out, whereby the angle between the fixed scroll 9 and the orbiting scroll 11 is adjusted.

In this positioning method, since the diameters dp and Dp and the distance 1 are set so as to satisfy the relational expression (Dp-dp) / 1 = α, the centering pin 40, the scroll-side pin hole 9d and the frame Positioning can be performed by adjusting the angle only by setting the diameter of the side pin hole 3d. That is, since the phases are merely shifted using the gap between the centering pin 40 and the two pin holes 9d and 3d, the diameters of the scroll-side pin hole 9d and the frame-side pin hole 3d are kept as they are, The angle can be easily adjusted with a certain degree of freedom by changing only the diameter of the.

Even in the case of complete meshing, as shown in FIGS. 3 and 4, when the orbiting scroll 11 starts to traverse the discharge port 14, the pressure balance of the compression chambers P on both sides of the central compression chamber P is lost. Considering that the gap ΔC is generated at the inner ends of both scrolls, including preventing the interference due to the thermal expansion of the central portion, the interference is prevented even if rotated by α.

Next, a second embodiment of the scroll compressor which is a scroll type fluid machine according to the present invention will be described with reference to FIG.

The difference between the second embodiment and the first embodiment is that the positioning of the fixed scroll 9 and the orbiting scroll 11 in the first embodiment is performed by using the frame 3 and the frame side pin holes 3 d formed in the fixed scroll 9. While the centering pin 40 is inserted into the scroll-side pin hole 9d, the second embodiment uses the same fixed scroll 9 and the orbiting scroll 11 as in the prior art, and their positioning is shown in FIG. As described above, the keys which are orthogonal to each other and function as the rotation preventing mechanism are shifted to the phase delay angle α.
Oldham ring formed by shifting only (Oldham mechanism)
50.

That is, in the second embodiment, as a positioning mechanism for the fixed scroll 9 and the orbiting scroll 11, the orbiting side key 50a of the Oldham ring 50 is rotated by 90 ° about the axis with respect to the predetermined radial direction Y. In the radial direction further deviated from the direction by the phase delay angle α. The orbiting side key groove 1 of the orbiting scroll 11 is attached to the orbiting side key 50a of the Oldham ring 50.
1c is fitted, and the orbiting scroll 11 is attached. The frame-side key 50 b is formed so as to protrude in a predetermined radial direction Y and is fitted into the frame-side key groove 3 a of the frame 3, as in the related art.

In this scroll compressor, the orbiting side key 5
0a is formed in the radial direction further shifted by a phase delay angle α from the direction rotated by 90 ° about the axis with respect to the predetermined radial direction Y, so that the turning key 50a and the turning key groove 11c are formed. The orbiting scroll 11 fitted and attached to the Oldham ring 50 is displaced by a phase delay angle α. That is, the Oldham ring 50 has both functions of a rotation preventing mechanism and a positioning mechanism, and merely by replacing the Oldham ring 50, the orbiting scroll 11
Can be adjusted.

Next, a third embodiment of the scroll compressor which is a scroll type fluid machine according to the present invention will be described with reference to FIGS.

The difference between the third embodiment and the first embodiment is that, in the first embodiment, the fixed-side spiral body 9b and the revolving-side spiral body 11b are engaged with each other with a phase shift of 180 ° as in the prior art. Using the fixed scroll 9 and the orbiting scroll 11 machined as
Only the phase adjustment is performed by rotating only the phase delay angle α. In the third embodiment, however, the adjustment by the rotation as described above is not performed, and as shown in FIG. The point is that the orbiting scroll in which the orbiting side spiral body 61a is processed in advance by an involute curve shifted by the phase delay angle α in advance is incorporated in the fixed scroll 9 similar to the above.

That is, in the third embodiment, the fixed scroll member 9b of the fixed scroll 9 is in a state where the scroll pin hole 9d is coaxially aligned with the frame pin hole 3d of the frame 3 as in the first embodiment. As shown in FIG. 7, the turning-side spiral body 61a is converted into point sequence data (profile data) of a numerically controlled machining device by rotational coordinate conversion in which a coordinate axis is rotated by a phase delay angle α in advance. Machined based on

The point sequence data is changed according to the following two relational expressions. X = xcosα + ysinα Y = −xsinα + ycosα Here, (x, y) is point sequence data when there is no deviation in angle, and (X, Y) is point sequence data when the angle is deviated.

In the third embodiment, since the orbiting scroll of the orbiting spiral body 61a shifted in advance by the phase delay angle α in the machining stage is provided, the angle adjustment at the time of assembly is not required. In addition, since the phase delay angle α for shifting the turning-side spiral 61a is determined from the above relational expression, the numerically controlled machining device can also process the turning-side spiral 61a having a complicated shape such as an involute curve. It is.

The present invention also includes the following embodiments. (1) In the second embodiment, the turning key 50a is formed in the Oldham ring 50 and the turning key groove 11c is formed in the turning scroll 11, but the key groove is formed in the Oldham ring, and the key is formed in the turning scroll. May be formed. (2) The orbiting scroll 11 is formed of a material having a larger coefficient of thermal expansion than the fixed scroll 9, but may be applied to a case where the fixed scroll is formed of a material having a larger coefficient of thermal expansion.

(3) In the third embodiment, only the orbiting scroll member 11b of the orbiting scroll 11 is processed and formed with a phase lag angle α shifted in advance. One or both scrolls may be processed so as to be shifted from each other by the phase delay angle α. For example, only the fixed-side spiral body of the fixed scroll may be processed by being shifted by the phase delay angle α in advance.

(4) In the first embodiment, the shape of the frame-side pin hole 3d and the scroll-side pin hole 9d is circular in cross section, but the circumferential distance Dp of the opening is determined by the relational expression (Dp-dp) / l = α. Is satisfied, other cross-sectional shapes may be used. For example,
It may have an elliptical cross section or a long hole shape.

(5) In the second embodiment, the turning key 50
Although the Oldham ring 50 having the a and the frame-side key 50b is adopted, an Oldham mechanism having another key and a key groove structure may be adopted. For example, FIG.
As shown in FIG. 7, the turning-side key 100a and the frame-side key 100 are formed so as to protrude radially outward.
An Oldham ring 100 having b may be used. In this case, a revolving-side key groove and a frame-side key groove are formed on the revolving scroll and the frame, respectively, corresponding to the revolving-side key 100a and the frame-side key 100b.

(6) In each of the above embodiments, the fixed scroll is fixed and the orbiting scroll is set to orbit relative to the fixed scroll. However, both scrolls are made of materials having different coefficients of thermal expansion. If so, the present invention can be similarly applied to a case in which both scrolls rotate and the other turns.

[0067]

According to the present invention, the following effects can be obtained. (1) In the scroll type fluid machine according to the present invention, the spiral bodies are engaged with each other at a position further shifted by an angle corresponding to a difference in thickness of the spiral bodies during thermal expansion from a state where the spiral bodies are shifted by 180 ° in phase. Therefore, even if the temperature rises during turning, no gap or interference occurs between the two spiral bodies, and a good meshing state between the two spiral bodies can be easily obtained.

(2) According to the scroll-type fluid machine and the method of manufacturing the same according to the present invention, the respective spiral bodies are
From the state where the phase is shifted by 180 °, it meshes with the position further shifted by the phase delay angle α calculated by the relational expression α = R · t · Δ / b. Since the body is displaced, no gap or interference occurs between the spiral bodies even at a high temperature, and it is possible to prevent a decrease in compression performance such as leakage of fluid. That is, even in the case of both scrolls made of different materials, a good meshing state can be obtained during operation, and high efficiency compression performance can be maintained.

(3) Further, since the intersecting radial direction is set to a direction in which the phase is delayed by the phase delay angle α with respect to the radial direction orthogonal to the predetermined radial direction, Just attach the scroll to the Oldham mechanism by fitting the key and key groove of each other,
Can be shifted by the phase delay angle α. That is, the Oldham mechanism can have both functions of the rotation preventing mechanism and the phase shifting means, and the adjustment of the Oldham mechanism can easily adjust the mounting angle of the other scroll.

(4) The spiral of the other scroll is preliminarily processed to a position shifted by a phase delay angle α from a position where the scroll is engaged with the spiral of the fixed scroll by 180 °. This eliminates the need to shift the engagement positions of the spiral bodies during assembly.

(5) In the method for manufacturing a scroll-type fluid machine, the circumferential distance Dp of the opening and the diameter d
By setting p and the distance l so as to satisfy the relational expression (Dp-dp) / l = α, the angle can be adjusted only by setting the dimensions of the centering pin, the scroll-side pin hole, and the stationary member-side pin hole. Position. Therefore, since only the phase is shifted by utilizing the gap between the centering pin and both pin holes, by changing the diameter of the centering pin only by keeping the dimensions of the scroll side pin hole and the stationary member side pin hole constant, Angle adjustment can be performed with a certain degree of freedom.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view after a thermal expansion and a cross-sectional view before a thermal expansion showing a fixed-side spiral body and a revolving-side spiral body in a first embodiment of a scroll compressor that is a scroll-type fluid machine according to the present invention.

FIG. 2 is an explanatory diagram showing a positional relationship between a centering pin and a pin hole for describing a positioning method in a first embodiment of a scroll compressor as a scroll type fluid machine according to the present invention.

FIG. 3 is an explanatory diagram showing engagement of a fixed-side spiral body and a revolving-side spiral body in the first embodiment of the scroll compressor that is a scroll-type fluid machine according to the present invention.

FIG. 4 is a sectional view of a main part showing a gap at an inner end of the scroll in the first embodiment of the scroll compressor which is a scroll type fluid machine according to the present invention.

FIG. 5 is a front view showing an Oldham ring in a second embodiment of the scroll compressor which is a scroll type fluid machine according to the present invention.

FIG. 6 is a cross-sectional view after a thermal expansion and a cross-sectional view before a thermal expansion showing a fixed-side spiral body and a revolving-side spiral body in a third embodiment of a scroll compressor that is a scroll-type fluid machine according to the present invention.

FIG. 7 is an explanatory diagram showing rotation coordinate conversion of point sequence data of a numerically controlled machining device for machining a turning-side spiral in a third embodiment of a scroll compressor as a scroll-type fluid machine according to the present invention.

FIG. 8 is a sectional view showing a conventional example of a scroll compressor which is a scroll type fluid machine according to the present invention.

FIG. 9 is a cross-sectional view showing a fixed-side spiral body and a revolving-side spiral body in a conventional example of a scroll compressor as a scroll-type fluid machine according to the present invention after thermal expansion and before thermal expansion.

FIG. 10 is a front view of a main part showing a positional relationship between a frame and an Oldham ring in a conventional example of a scroll compressor which is a scroll type fluid machine according to the present invention.

FIG. 11 is a main part front view showing a positional relationship between a fixed scroll and an orbiting scroll in a conventional example of a scroll compressor which is a scroll type fluid machine according to the present invention.

FIG. 12 is an explanatory diagram showing a relationship between a thickness of a spiral body and a phase delay angle α in a scroll type fluid machine according to the present invention.

FIG. 13 is an explanatory view showing an overall shape of a spiral body in the scroll fluid machine according to the present invention.

FIG. 14 is an explanatory diagram showing engagement of spiral bodies in a scroll type fluid machine according to the present invention.

FIG. 15 is an explanatory diagram showing a tip shape of a spiral body in a scroll type fluid machine according to the present invention.

FIG. 16 is a schematic front view showing the positional relationship between the fixed scroll and the orbiting scroll during orbiting in the scroll fluid machine according to the present invention.

FIG. 17 is a schematic perspective view showing an Oldham ring in another embodiment of the scroll fluid machine according to the present invention.

[Explanation of symbols]

 Reference Signs List 3 frame (stationary member) 3d frame-side pin hole (stationary member-side pin hole) 4 scroll-type compression mechanism 9 fixed scroll (one scroll) 9a fixed-side end plate 9b fixed-side scroll 9d scroll-side pin hole 11 orbiting scroll ( 11a Revolving-side end plate 11b Revolving-side spiral body 11c Revolving-side keyway 12 Rotation-preventing mechanism 40 Centering pin 50, 100 Oldham ring (Oldham mechanism) 50a, 100a Revolving-side key 50b, 100b Frame-side key 61a Revolving Side spiral body Dp Diameter of scroll side pin hole (circumferential distance of opening) dp Diameter of centering pin K Base circle

Claims (6)

[Claims] 1. A scroll having one end and a scroll on the end plate, each of which has an involute curve drawn by an involute curve defined by a base circle having the same radius, and a rotation preventing mechanism for preventing rotation of the other scroll. In a scroll-type fluid machine that is rotatable in a deflected state and rotatable at a predetermined radius by an eccentric drive mechanism to enable relative orbital movement between scrolls, the one scroll has a coefficient of thermal expansion γ is manufactured of a material _f, the other scroll is made are produced with a material of the thermal expansion coefficient gamma _f larger thermal expansion coefficient gamma _m, representing the radius of the base circle b, in the radial direction of said end plate the size R, a representative temperature in the typical dimension R at the time of operation t, the coefficient of thermal expansion difference which is a difference between the thermal expansion coefficient gamma _m and the thermal expansion coefficient gamma _f delta
When the spiral bodies are shifted from each other by 180 °, the spiral bodies are shifted to a position further shifted by a phase delay angle α (rad) calculated by the following relational expression α = R · t · Δ / b. A scroll type fluid machine comprising a phase shifting means for matching. 2. The scroll-type fluid machine according to claim 1, wherein the phase shifter is provided between the end plate of the one scroll and the end plate of the other scroll, and the both end plates are formed by a key and a keyway. An Oldham mechanism for slidably guiding each other through a structure in a predetermined radial direction and a radial direction intersecting with the predetermined direction, wherein the other scroll key or key groove extends the spiral bodies of each other by 180 °. Assuming that the phases are shifted, they are arranged in a radial direction orthogonal to the predetermined radial direction, and the Oldham mechanism is configured such that the intersecting radial direction is the phase with respect to a radial direction orthogonal to the predetermined radial direction. A scroll type fluid machine wherein the phase is set in a direction delayed by a delay angle α. 3. The scroll-type fluid machine according to claim 1, wherein the phase shift means is configured to shift the spiral body of the other scroll into mesh with the spiral body of the one scroll by 180 °. A scroll-type fluid machine, which is machined in advance at a position shifted by the phase delay angle α. 4. A scroll having one scroll and another scroll in which a spiral body which draws an involute curve defined by a base circle having the same radius is provided on an end plate, and the other scroll is prevented from rotating by a rotation preventing mechanism. In a scroll-type fluid machine, which is rotatable in a deflected state and is rotatable at a predetermined radius by an eccentric drive mechanism, and enables relative orbital movement between the scrolls, the other scroll and the one scroll Has the above-mentioned spiral bodies having different thicknesses during thermal expansion, and meshes these spiral bodies at a position further shifted by an angle corresponding to the difference in thickness from a state shifted in phase by 180 °. A scroll-type fluid machine. 5. A scroll, which draws an involute curve defined by a base circle having the same radius as each other, rotates one scroll and the other scroll, each of which is erected on an end plate, by rotating the scrolls with each other. A method of manufacturing a scroll-type fluid machine for assembling the other scroll so as to be able to swivel in a hindered state, wherein the one scroll is made of a material having a coefficient of thermal expansion γ _f , and the other scroll is formed of the thermal expansion. it is manufactured of a material rate gamma _f larger thermal expansion coefficient gamma _m, radius b of the base circle, R the radius direction of the representative dimension of the end plate, a representative temperature in the typical dimension R at the time of operation t the thermal expansion coefficient difference is the difference between the thermal expansion coefficient gamma _m and the thermal expansion coefficient gamma _f delta
When the spiral bodies are shifted from each other by 180 °, the spiral bodies are shifted to a position further shifted by a phase delay angle α (rad) calculated by the following relational expression α = R · t · Δ / b. A method for manufacturing a scroll-type fluid machine, comprising a positioning step for matching. 6. The method for manufacturing a scroll type fluid machine according to claim 5, wherein said one scroll is provided with said spiral bodies by 180.
Assuming that the meshing is performed by shifting the phase by ゜, a scroll-side pin hole having a circumferential distance Dp of the opening is formed at a position apart from the axis by a predetermined radial distance l, and the one scroll is fixed. In the member, a stationary member side pin hole having the same diameter as the scroll side pin hole is formed at a position separated by a distance 1 in the predetermined radial direction from an axis, and the positioning step includes: The stationary member and the stationary member side have the same axis, and a centering pin having a diameter dp is inserted into the scroll side pin hole and the stationary member side pin hole. A scroll rotation step of rotating one of the scrolls around the axis to a position sandwiching the centering pin on the surface; and after the scroll rotation step, the one scroll is stationary in this state. A scroll fixing step of fixing the material to a material and pulling out the centering pin, wherein the circumferential distance Dp, the diameter dp, and the distance l of the opening are represented by the following relational expression (Dp-dp) / l = α. A method for manufacturing a scroll-type fluid machine, characterized in that: