JP6679633B2 - Scroll fluid machinery - Google Patents

Description

  The present invention relates to a scroll fluid machine.

  In general, there is known a scroll fluid machine in which a fixed scroll member having a spiral wall body provided on an end plate and an orbiting scroll member are engaged with each other to perform an orbital orbiting motion to compress or expand a fluid.

  As such a scroll fluid machine, a so-called step scroll compressor as disclosed in Patent Document 1 is known. In this stepped scroll compressor, stepped portions are provided on the tooth top surface and the tooth bottom surface of the spiral wall bodies of the fixed scroll and the orbiting scroll, respectively, at positions along the spiral direction. The height on the side is higher than the height on the inner circumference side. Since the step scroll compressor is compressed not only in the circumferential direction of the wall but also in the height direction (three-dimensional compression), compared to a general scroll compressor without a step (two-dimensional compression) , The displacement can be increased and the compressor capacity can be increased.

JP, 2005-55173, A

  However, the step scroll compressor has a problem that the fluid leakage at the step is large. In addition, there is a problem that stress concentrates on the root portion of the step and the strength decreases.

On the other hand, the inventors are considering providing a continuous inclined portion instead of the stepped portion provided on the wall body and the end plate.
However, even if the inclined portion is provided, it has not been established in the past how appropriate the inclined portion should be.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a scroll fluid machine having an inclined portion on a wall body and an end plate that can effectively exhibit performance.

In order to solve the above problems, the scroll fluid machine of the present invention employs the following means.
That is, the scroll fluid machine according to the present invention includes a first scroll member in which a spiral first wall body is provided on a first end plate, and a second end plate disposed so as to face the first end plate. A scroll fluid machine comprising: a second scroll member provided on a spiral-shaped second wall body; the second wall body meshes with the first wall body and relatively revolves around; The distance between the facing surfaces of the first end plate and the second end plate facing each other is such that an inclined portion is continuously reduced from the outer peripheral side of the first wall body and the second wall body toward the inner peripheral side. The inclined portion is provided over a range of 180 ° or more around the center of the spiral, and the groove portion formed at the tooth tip of the first wall body and the second wall body corresponding to the inclined portion, opposing teeth while being pressed from the back to the intruded compressed fluid in the groove portion Tip seal in contact with follow the change in the tip clearance variation ΔT to seal the fluid is provided during turning movement, the turning radius of the scroll member to pivot [rho, and the slope of the spiral direction of the inclined portion φ when the tip clearance variation ΔT is defined by the following equation,
ΔT = 2ρ × tanφ
The tip clearance change amount ΔT is 50% or less of the height dimension of the tip seal in the height direction of the wall body.

Since the inclined portion in which the distance between the facing surfaces of the first end plate and the second end plate continuously decreases from the outer peripheral side to the inner peripheral side of the wall body is provided, the fluid sucked from the outer peripheral side is As it goes toward the inner peripheral side, not only is it compressed by the reduction of the compression chamber corresponding to the spiral shape of the wall body, but it is further compressed by the reduction of the distance between the facing surfaces between the end plates.
Since the inclined portion is provided, the tip clearance between the tooth tip and the tooth bottom changes according to the turning movement. The tip clearance change amount ΔT according to the orbiting motion is as follows when the orbiting radius of the orbiting scroll member is ρ and the inclination of the inclined portion in the spiral direction is φ.
ΔT = 2ρ × tanφ
The tip seal moves back and forth in the height direction from the groove portion by an amount corresponding to the tip clearance change amount ΔT. Therefore, if the amount of change in tip clearance ΔT is large, the tip seal may come off from the groove.
Therefore, the tip clearance change amount ΔT is set to 50% or less of the height dimension of the tip seal to prevent the tip seal from falling off.
It is more preferable that the tip clearance change amount ΔT is 20% or less of the height dimension of the tip seal.

Also, the scroll fluid machine of the present invention includes a first scroll member having a first end plate on which a spiral first wall is provided, and a second end plate disposed so as to face the first end plate. A scroll fluid machine provided with a second scroll-shaped wall body, and a second scroll member that engages with the first wall body and makes a relative revolution movement relative to the first wall body. An inclined portion is provided in which the distance between the facing surfaces of the first end plate and the second end plate continuously decreases from the outer peripheral side to the inner peripheral side of the first wall body and the second wall body. The inclined portion is provided over a range of 180 ° or more around the center of the spiral, and when the orbiting radius of the orbiting scroll member is ρ and the inclination of the inclined portion in the spiral direction is φ, the tip clearance changes. The quantity ΔT is defined by
ΔT = 2ρ × tanφ
A value obtained by dividing the tip clearance change amount ΔT by the height of the outermost periphery of the wall body is 0.01 or less so as to maintain the oil film seal between the tip clearances .

Since the inclined portion in which the distance between the facing surfaces of the first end plate and the second end plate continuously decreases from the outer peripheral side to the inner peripheral side of the wall body is provided, the fluid sucked from the outer peripheral side is As it goes toward the inner peripheral side, not only is it compressed by the reduction of the compression chamber corresponding to the spiral shape of the wall body, but it is further compressed by the reduction of the distance between the facing surfaces between the end plates.
Since the inclined portion is provided, the tip clearance between the tooth tip and the tooth bottom changes according to the turning movement. The tip clearance change amount ΔT according to the orbiting motion is as follows when the orbiting radius of the orbiting scroll member is ρ and the inclination of the inclined portion in the spiral direction is φ.
ΔT = 2ρ × tanφ
An oil film seal made of lubricating oil is formed between the tooth tip and the tooth bottom. However, if the tip clearance change amount ΔT becomes large, the oil film seal between the tooth tip and the tooth bottom may be broken, and the sealing performance of the compression chamber may be reduced, resulting in a reduction in efficiency.
As a result of diligent studies by the present inventors, if the value obtained by dividing the amount of change in tip clearance ΔT by the height of the outermost periphery of the wall is 0.01 or less, the oil film seal is maintained and a large decrease in performance is not observed. , Found that the desired efficiency can be maintained.

Also, the scroll fluid machine of the present invention includes a first scroll member having a first end plate on which a spiral first wall is provided, and a second end plate disposed so as to face the first end plate. A scroll fluid machine provided with a second scroll-shaped wall body, and a second scroll member that engages with the first wall body and makes a relative revolution movement relative to the first wall body. An inclined portion is provided in which the distance between the facing surfaces of the first end plate and the second end plate continuously decreases from the outer peripheral side to the inner peripheral side of the first wall body and the second wall body. is, the inclined portion is provided over a range of more than 180 ° about the center of the spiral, the tip clearance between the tooth bottom of the end plate and the tooth tip of the wall body, the teeth tip and tooth bottom to avoid interference, assembled twist angle around the center of the scroll member according to the error Characterized in that it is set larger than the tip clearance decrease amount based.

Since the inclined portion in which the distance between the facing surfaces of the first end plate and the second end plate continuously decreases from the outer peripheral side to the inner peripheral side of the wall body is provided, the fluid sucked from the outer peripheral side is As it goes toward the inner peripheral side, not only is it compressed by the reduction of the compression chamber corresponding to the spiral shape of the wall body, but it is further compressed by the reduction of the distance between the facing surfaces between the end plates.
In the scroll fluid machine, when the first scroll member and the second scroll member are assembled, an assembly error inevitably occurs due to the dimensional accuracy of the Oldham ring and the positional accuracy of the centering pin and the like. When an assembling error occurs, the scroll member is twisted about its center, and the tip clearance between the tip and the bottom of the inclined portion is reduced based on the twist angle.
Therefore, the tip clearance between the tooth tip and the tooth bottom is set to be larger than the amount of the tip clearance reduction based on the twist angle around the center of the scroll member due to an assembly error to avoid interference between the tooth tip and the tooth bottom. And

  By setting the amount of change in tip clearance ΔT (= 2ρ × tan φ) to 50% or less of the height dimension of the tip seal, it is possible to prevent the tip seal from falling off. Thereby, even if the wall body and the end plate have the inclined portions, the performance can be exhibited.

  By setting the value obtained by dividing the amount of change in tip clearance ΔT (= 2ρ × tanφ) by the height of the outermost circumference of the wall to be 0.01 or less, the oil film seal is maintained and no major deterioration in performance is observed. The performance of can be maintained.

  By setting the tip clearance between the tooth tip and the tooth bottom to be larger than the amount of tip clearance reduction based on the twist angle around the center of the scroll member due to an assembly error, interference between the tooth tip and the tooth bottom can be avoided. .

The fixed scroll and the orbiting scroll of the scroll compressor concerning one Embodiment of this invention are shown, (a) is a longitudinal cross-sectional view, (b) is the top view seen from the wall body side of a fixed scroll. It is the perspective view which showed the orbiting scroll of FIG. It is a top view showing an end plate flat part provided in a fixed scroll. It is a top view showing a wall body flat part provided in a fixed scroll. It is a schematic diagram which shows the wall body extended and displayed in the spiral direction. It is the elements on larger scale which expanded and showed the area | region of the code | symbol Z of FIG.1 (b). 6A and 6B show the tip seal gap in the portion shown in FIG. 6, FIG. 6A is a side view showing a state where the tip seal gap is relatively small, and FIG. 6B shows a state where the tip seal gap is relatively large. It is a side view. 10 is a graph showing a rate of change in efficiency with respect to a change in tip clearance according to the second embodiment of the present invention. It is between the tooth tip and the tooth bottom, (a) is a partial enlarged sectional view showing a state in which an oil film seal is formed, and (b) is a partially enlarged sectional view showing a state in which the oil film seal is broken. is there. It is the top view which showed the fixed scroll and orbiting scroll which concern on 3rd Embodiment of this invention, and was seen from the wall body side of a fixed scroll. A modification is shown, (a) is a longitudinal cross-sectional view showing a combination with a scroll having no step portion, and (b) is a vertical cross-sectional view showing a combination with a stepped scroll.

[First Embodiment]
Hereinafter, a first embodiment according to the present invention will be described with reference to the drawings.
FIG. 1 shows a fixed scroll (first scroll member) 3 and an orbiting scroll (second scroll member) 5 of a scroll compressor (scroll fluid machine) 1. The scroll compressor 1 is used as a compressor that compresses a gas refrigerant (fluid) that performs a refrigeration cycle such as an air conditioner.

  The fixed scroll 3 and the orbiting scroll 5 are metal compression mechanisms made of aluminum alloy or iron, and are housed in a housing (not shown). The fixed scroll 3 and the orbiting scroll 5 suck the fluid introduced into the housing from the outer peripheral side, and discharge the compressed fluid from the discharge port 3c at the center of the fixed scroll 3 to the outside.

  The fixed scroll 3 is fixed to the housing, and as shown in FIG. 1A, a substantially disk-shaped end plate (first end plate) 3a and one end surface of the end plate 3a. The spiral wall body (first wall body) 3b is provided. The orbiting scroll 5 includes a substantially disk-shaped end plate (second end plate) 5a, and a spiral wall body (second wall body) 5b that is erected on one side surface of the end plate 5a. . The spiral shape of each of the walls 3b and 5b is defined using, for example, an involute curve or Archimedes curve.

  The fixed scroll 3 and the orbiting scroll 5 are engaged with each other with their centers separated by an orbiting radius ρ and the phases of the wall bodies 3b and 5b are shifted by 180 ° so that the tooth tips and the tooth bottoms of the wall bodies 3b and 5b of both scrolls are kept at room temperature. Is assembled so as to have a slight clearance in the height direction (chip clearance). As a result, a plurality of pairs of compression chambers formed by being surrounded by the end plates 3a, 5a and the walls 3b, 5b are formed between the scrolls 3 and 5 symmetrically with respect to the scroll center. The orbiting scroll 5 revolves around the fixed scroll 3 by a rotation preventing mechanism such as an Oldham ring (not shown).

  As shown in FIG. 1 (a), the distance L between the facing surfaces between the opposite end plates 3a, 5a continuously decreases from the outer peripheral side to the inner peripheral side of the spiral wall bodies 3b, 5b. Section is provided.

  As shown in FIG. 2, the wall body 5b of the orbiting scroll 5 is provided with a wall body inclined portion 5b1 whose height continuously decreases from the outer peripheral side toward the inner peripheral side. An end plate inclined portion 3a1 (see FIG. 1 (a)) inclined according to the inclination of the wall inclined portion 5b1 is provided on the tooth bottom surface of the fixed scroll 3 where the tooth tips of the wall inclined portion 5b1 face each other. There is. The wall inclined portion 5b1 and the end plate inclined portion 3a1 form a continuous inclined portion. Similarly, the wall body 3b of the fixed scroll 3 is also provided with a wall body inclined portion 3b1 whose height continuously inclines from the outer peripheral side toward the inner peripheral side, and faces the tooth tips of the wall body inclined portion 3b1. The end plate inclined portion 5a1 is provided on the end plate 5a of the orbiting scroll 5.

  Note that the continuous meaning in the inclined portion in the present embodiment is not limited to a smoothly connected inclination, and small steps that are inevitably generated during processing are connected in a stepwise manner. When the part is viewed as a whole, it also includes one that is continuously inclined. However, it does not include large steps such as so-called step scrolls.

  The wall inclined portions 3b1 and 5b1 and / or the end plate inclined portions 3a1 and 5a1 are coated. Examples of the coating include manganese phosphate treatment and nickel phosphorus plating.

As shown in FIG. 2, wall flat portions 5b2 and 5b3 having a constant height are provided on the innermost peripheral side and the outermost peripheral side of the wall body 5b of the orbiting scroll 5, respectively. . The wall flat portions 5b2 and 5b3 are provided over a region of 180 ° around the center O2 (see FIG. 1A) of the orbiting scroll 5. At the positions where the wall flat portions 5b2, 5b3 and the wall inclined portion 5b1 are connected to each other, wall inclined connection portions 5b4, 5b5, which are bent portions, are provided.
Similarly, the bottoms of the end plate 5a of the orbiting scroll 5 are also provided with end plate flat portions 5a2 and 5a3 having a constant height. These end plate flat portions 5a2 and 5a3 are also provided over the area of 180 ° around the center of the orbiting scroll 5. At the positions where the end plate flat portions 5a2 and 5a3 and the end plate inclined portion 5a1 are connected, end plate inclined connection portions 5a4 and 5a5, which are bent portions, are provided, respectively.

  As shown by hatching in FIGS. 3 and 4, also for the fixed scroll 3, similarly to the orbiting scroll 5, the end plate flat portions 3a2, 3a3, the wall body flat portions 3b2, 3b3, the end plate inclined connection portions 3a4, 3a5. And wall inclined connection portions 3b4 and 3b5 are provided.

FIG. 5 shows the wall bodies 3b and 5b which are extended and displayed in the spiral direction. As shown in the drawing, the innermost wall side flat portions 3b2 and 5b2 are provided over a distance D2, and the outermost circumferential wall flat portions 3b3 and 5b3 are provided over a distance D3. Each of the distance D2 and the distance D3 has a length corresponding to a region of 180 ° (180 ° or more and 360 ° or less, preferably 210 ° or less) around the centers O1 and O2 of the scrolls 3 and 5, respectively. Between the innermost flat wall portions 3b2, 5b2 and the outermost flat wall portions 3b3, 5b3, wall inclined portions 3b1, 5b1 are provided over a distance D1. When the height difference between the innermost wall flat portions 3b2, 5b2 and the outermost wall flat portions 3b3, 5b3 is h, the inclination φ of the wall inclined portions 3b1, 5b1 is given by the following equation.
φ = tan ⁻¹ (h / D1) ・ ・ ・ (1)
In this way, the inclination φ in the inclined portion is constant with respect to the circumferential direction in which the spiral wall bodies 3b and 5b extend. The distance D1 is longer than the distance D2 and longer than the distance D3.
For example, in this embodiment, the specifications of the scrolls 3 and 5 are as follows.
(1) Turning radius ρ [mm]: 2 or more and 15 or less, preferably 3 or more and 10 or less (2) Number of turns of the wall bodies 3b and 5b: 1.5 or more and 4.5 or less, preferably 2.0 or more and 3.5. The following (3) height difference h [mm]: 2 or more and 20 or less, preferably 5 or more and 15 or less (4) h / Lout (wall height on the outermost peripheral side):
0.05 or more and 0.35 or less, preferably 0.1 or more and 0.25 or less (5) Angle range of the inclined portion (angle range corresponding to the distance D1) [°]:
180 or more and 1080 or less, preferably 360 or more and 720 or less (6) Angle φ [°] of the inclined portion: 0.2 or more and 4 or less, preferably 0.5 or more and 2.5 or less

  FIG. 6 shows an enlarged view of the area indicated by reference symbol Z in FIG. As shown in FIG. 6, a tip seal 7 is provided on the tooth tip of the wall body 3 b of the fixed scroll 3. The tip seal 7 is made of resin and contacts the bottom of the end plate 5a of the orbiting scroll 5 facing the tip seal 7 to seal the fluid. The tip seal 7 is housed in a tip seal groove 3d formed circumferentially in the tooth tips of the wall 3b. The compressed fluid enters into the tip seal groove 3d, presses the tip seal 7 from the back surface and pushes the tip seal 7 toward the tooth bottom side to bring it into contact with the opposing tooth bottom. Note that tip seals are similarly provided on the tips of the walls 5b of the orbiting scroll 5.

  When both scrolls 3 and 5 relatively perform a revolving orbiting motion, the positions of the tooth tip and the tooth bottom are relatively displaced by the orbiting diameter (orbiting radius ρ × 2). Due to the positional deviation between the tooth tip and the tooth bottom, the tip clearance between the tooth tip and the tooth bottom changes in the inclined portion. The chip clearance change amount Δh [mm] is, for example, 0.05 or more and 1.0 or less, preferably 0.1 or more and 0.6 or less. For example, FIG. 7A shows that the tip clearance T is small, and FIG. 7B shows that the tip clearance T is large. Even if the tip clearance T changes due to the swiveling motion, the tip seal 7 is pressed against the tooth bottom side of the end plate 5a from the back surface, so that the tip seal 7 can follow and seal.

As shown in FIG. 7, the tip clearance change amount ΔT, in which the tip clearance T changes during one turn, can be expressed by the following equation.
ΔT = 2ρ × tanφ (2)
Here, ρ is the turning radius.

  The amount of change ΔT in the tip clearance is set to 50% or less of the height dimension Hc of the tip seal in the height direction of the walls 3b and 5b.

The scroll compressor 1 described above operates as follows.
The orbiting scroll 5 revolves around the fixed scroll 3 by a drive source such as an electric motor (not shown). As a result, the fluid is sucked from the outer peripheral sides of the scrolls 3 and 5, and the fluid is taken into the compression chamber surrounded by the wall bodies 3b and 5b and the end plates 3a and 5a. The fluid in the compression chamber is sequentially compressed as it moves from the outer peripheral side to the inner peripheral side, and finally the compressed fluid is discharged from the discharge port 3c formed in the fixed scroll 3. When the fluid is compressed, the inclined portions formed by the end plate inclined portions 3a1 and 5a1 and the wall inclined portions 3b1 and 5b1 are also compressed in the height direction of the walls 3b and 5b to perform three-dimensional compression. Be seen.

According to this embodiment, the following operational effects are exhibited.
Therefore, the tip clearance change amount ΔT is set to 50% or less of the height dimension Hc of the tip seal 7. This prevents the tip seal 7 from coming off the tip seal groove 3d even if the tip seal 7 moves back and forth in the height direction from the tip seal groove 3d by the amount corresponding to the tip clearance change amount ΔT. It is possible to prevent the tip seal 7 from falling off.
The tip clearance change amount ΔT may be 20% or less of the height dimension Hc of the tip seal 7.

[Second Embodiment]
Next, a second embodiment of the present invention will be described.
The present embodiment is different in the concept of setting the upper limit of the tip clearance change amount ΔT, and is the same in other configurations. Therefore, in the following description, only the differences from the first embodiment will be described, and the other configurations are the same, so the description will be omitted.

In the present embodiment, ΔT / Lout, which is a value obtained by dividing the amount of change in tip clearance ΔT by the height of the outermost periphery of the walls 3b and 5b (see the reference Lout in FIG. 2), is set to 0.01 or less. . The reason will be described with reference to FIGS. 8 and 9.
In FIG. 8, the horizontal axis is ΔT / Lout, and the vertical axis is the efficiency change rate. The efficiency change ratio is the ratio of the efficiency at a predetermined ΔT / Lout with respect to the case where the chip clearance change amount ΔT is zero, that is, the efficiency in the case of a so-called two-dimensional scroll in which there is no inclination of the wall height is 1. Show. As shown in FIG. 8, when ΔT / Lout is 0.01, the efficiency change rate decreases by less than 1%. Therefore, if ΔT / Lout is set to 0.01 or less, the decrease in the efficiency change rate can be suppressed to less than 1%.

As shown in FIG. 9A, when ΔT / Lout is in the range of 0.01 or less, the tip clearance T is set to a predetermined value or less so that the end plates 5a, 3a facing the tooth tips of the walls 3b, 5b. It is considered that the oil film seal OS formed by the lubricating oil is formed between the bottom of the tooth. Since the oil film seal OS is secured in the tip clearance T in this manner, fluid leakage in the compression chamber is reduced, and a decrease in efficiency change rate is reduced.
On the other hand, when ΔT / Lout is larger than 0.01, the tip clearance T becomes large, and the oil film is separated at the tip clearance T as shown in FIG. 9B, and the oil film seal OS (see FIG. 9A). And the fluid leaks in the compression chamber. As a result, the efficiency change rate is greatly reduced.

  As described above, according to the present embodiment, the desired efficiency can be maintained by maintaining the oil film seal OS between the tip clearances T by setting ΔT / Lout to 0.01 or less.

[Third Embodiment]
Next, a third embodiment of the present invention will be described.
In this embodiment, setting of the lower limit of the tip clearance T will be described. Other configurations are the same as those in the above-described embodiments. Therefore, in the following description, only the differences from each of the above-described embodiments will be described, and the other configurations are the same, so description thereof will be omitted. This embodiment can be used in combination with the first embodiment or the second embodiment.

In the present embodiment, the tip clearance T between the tooth tips of the walls 3b and 5b and the tooth bottoms of the end plates 5a and 3a is set in consideration of the twist angle δθ around the centers of the scrolls 3 and 5 due to an assembly error. There is. As shown in FIG. 10, when the scrolls 3 and 5 are assembled and operated, the twist angle δθ is unavoidably caused by an assembly error due to the dimensional accuracy of the Oldham ring, the positional accuracy of the centering pin, etc. It is caused by the play generated around the centers of 3 and 5. Note that FIG. 10 is a diagram similar to FIG. Since gas pressure in the compression chamber is applied during operation, rattling around the centers of the scrolls 3 and 5 causes the tooth tips at the inclined portions of the wall bodies 3b and 5b to come close to the tooth bottoms of the end plates 5a and 3a, resulting in tip clearance. T decreases. This tip clearance reduction amount δT is expressed by the following equation.
δT = r × δθ × tanφ (3)
Here, r is the radius on the outer peripheral side where the inclined portion starts, that is, the radius on the wall inclined connection portions 3b5, 5b5 (see FIGS. 2 and 5) on the outer peripheral sides of the wall bodies 3b, 5b. φ is the inclination at the inclined portion (see FIG. 5). The twist angle δθ can be obtained by actual measurement. Alternatively, it is also possible to individually measure the dimensions of the portion that causes the twist of the scroll, such as the dimensional accuracy of the Oldham ring and the positional accuracy of the centering pin, and calculate the twist angle δθ from these dimensions.

  In the present embodiment, when assembling the scrolls 3 and 5, the tip clearance reduction amount obtained from the above formula (3) considering the radius on the outer peripheral side where the inclined portion starts, the lip clearance reduction amount, and the inclination φ of the inclined portion. The tip clearance T is made larger than δT. Thereby, the interference between the tooth tip and the tooth bottom can be avoided.

In each of the above-described embodiments, the end plate inclined portions 3a1 and 5a1 and the wall body inclined portions 3b1 and 5b1 are provided on both scrolls 3 and 5, but they may be provided on either one.
Specifically, as shown in FIG. 11A, when one wall body (for example, the orbiting scroll 5) is provided with the wall body inclined portion 5b1 and the other end plate 3a is provided with the end plate inclined portion 3a1. The other wall body and the one end plate 5a may be flat.
Further, as shown in FIG. 11B, a shape combined with the conventional stepped shape, that is, the end plate inclined portion 3a1 is provided on the end plate 3a of the fixed scroll 3, while the end plate 5a of the orbiting scroll 5 is provided. You may combine with the shape provided with the step part.

  In each of the above-described embodiments, the wall flat portions 3b2, 3b3, 5b2, 5b3 and the end plate flat portions 3a2, 3a3, 5a2, 5a3 are provided, but the inner peripheral side and / or outer peripheral side flat portions are omitted. Then, the inclined portion may be provided so as to extend over the entire walls 3b and 5b.

  In each of the above embodiments, the scroll compressor is described, but the present invention can be applied to a scroll expander used as an expander.

1 Scroll compressor (scroll fluid machine)
3 Fixed scroll (first scroll member)
3a End plate (first end plate)
3a1 end plate inclined part 3a2 end plate flat part (inner peripheral side)
3a3 End plate flat part (outer peripheral side)
3a4 End plate inclined connection (inner side)
3a5 End plate inclined connection part (outer peripheral side)
3b wall (first wall)
3b1 Wall slope 3b2 Wall flat (inner side)
3b3 Wall flat part (outer peripheral side)
3b4 Wall inclined connection (inner side)
3b5 Wall slope connection (outer peripheral side)
3c Discharge port 3d Tip seal groove 5 Orbiting scroll (second scroll member)
5a End plate (second end plate)
5a1 end plate inclined part 5a2 end plate flat part (inner peripheral side)
5a3 End plate flat part (outer peripheral side)
5a4 End plate inclined connection part (inner circumference side)
5a5 End plate inclined connection part (outer peripheral side)
5b wall (second wall)
5b1 Wall sloped part 5b2 Wall flat part (inner side)
5b3 Wall flat part (outer peripheral side)
5b4 Wall slope connection (inner side)
5b5 Wall slope connection (outer peripheral side)
7 Tip seal Hc Tip seal height L L Face-to-face distance OS Oil film seal T Tip clearance ΔT Tip clearance change amount δT Tip clearance decrease amount φ Tilt δθ Twist angle

Claims (3)

A first scroll member in which a spiral first wall body is provided on the first end plate;
A spiral second wall body is provided on a second end plate arranged to face the first end plate, and the second wall body meshes with the first wall body to perform a relatively revolving motion. A second scroll member for performing,
A scroll fluid machine comprising:
The distance between the facing surfaces of the first end plate and the second end plate facing each other is such that an inclined portion is continuously reduced from the outer peripheral side of the first wall body and the second wall body toward the inner peripheral side. Is provided,
The inclined portion is provided over a range of 180 ° or more around the center of the spiral,
The groove formed in the tooth tip of the first wall body and the second wall body corresponding to the inclined portion is pressed from the back surface by the compressed fluid that has entered the groove portion, and swivels to the opposite tooth bottom. At the same time, a tip seal is provided that seals the fluid by contacting it while following the change in the tip clearance change amount ΔT .
The turning radius of the scroll member to pivot [rho, an inclination in the spiral direction of the inclined portion when the phi, the tip clearance variation ΔT is defined by the following equation,
ΔT = 2ρ × tanφ
The scroll fluid machine characterized in that the tip clearance change amount ΔT is 50% or less of the height dimension of the tip seal in the height direction of the wall body. A first scroll member in which a spiral first wall body is provided on the first end plate;
A spiral second wall body is provided on a second end plate arranged to face the first end plate, and the second wall body meshes with the first wall body to perform a relatively revolving motion. A second scroll member for performing,
A scroll fluid machine comprising:
The distance between the facing surfaces of the first end plate and the second end plate facing each other is such that an inclined portion is continuously reduced from the outer peripheral side of the first wall body and the second wall body toward the inner peripheral side. Is provided,
The inclined portion is provided over a range of 180 ° or more around the center of the spiral,
When the orbiting radius of the orbiting scroll member is ρ and the inclination of the inclined portion in the spiral direction is φ, the tip clearance change amount ΔT is defined by the following equation:
ΔT = 2ρ × tanφ
A value obtained by dividing the tip clearance change amount ΔT by the height of the outermost periphery of the wall body is 0.01 or less so as to maintain the oil film seal between the tip clearances. . A first scroll member in which a spiral first wall body is provided on the first end plate;
A spiral second wall body is provided on a second end plate arranged to face the first end plate, and the second wall body meshes with the first wall body to perform a relatively revolving motion. A second scroll member for performing,
A scroll fluid machine comprising:
The distance between the facing surfaces of the first end plate and the second end plate facing each other is such that an inclined portion is continuously reduced from the outer peripheral side of the first wall body and the second wall body toward the inner peripheral side. Is provided,
The inclined portion is provided over a range of 180 ° or more around the center of the spiral,
The twist angle around the center of the scroll member due to an assembly error so that the tip clearance between the tip of the wall and the bottom of the end plate avoids interference between the tip and the bottom. The scroll fluid machine is characterized in that it is set to be larger than the chip clearance reduction amount based on.

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