阅读说明：本技术 涡旋式压缩机 (Scroll compressor having a discharge port ) 是由 中井亮太 村上泰弘 水岛康夫 于 2018-06-07 设计创作，主要内容包括：涡旋式压缩机。涡旋式压缩机(10)具备具有固定涡旋件涡盘(52)的固定涡旋件(50)和具有可动涡旋件涡盘(62)的可动涡旋件(60)。固定涡旋件涡盘(52)的厚度即第2厚度(T2)大于可动涡旋件涡盘(62)的厚度即第1厚度(T1)。第1侧面间隙(G1)是可动涡旋件涡盘内线(63)和固定涡旋件涡盘外线(54)最接近时可动涡旋件涡盘内线(63)与固定涡旋件涡盘外线(54)之间的间隔。第2侧面间隙(G2)是可动涡旋件涡盘外线(64)和固定涡旋件涡盘内线(53)最接近时可动涡旋件涡盘外线(64)和固定涡旋件涡盘内线(53)之间的间隔。第2侧面间隙(G2)大于第1侧面间隙(G1)。(A scroll compressor is provided. A scroll compressor (10) is provided with a fixed scroll (50) having a fixed scroll (52) and a movable scroll (60) having a movable scroll (62). The thickness of the fixed scroll (52), i.e., the 2 nd thickness (T2), is greater than the thickness of the movable scroll (62), i.e., the 1 st thickness (T1). The 1 st flank gap (G1) is the distance between the movable scroll inner line (63) and the fixed scroll outer line (54) when the movable scroll inner line (63) and the fixed scroll outer line (54) are closest to each other. The 2 nd side gap (G2) is the distance between the movable scroll outer line (64) and the fixed scroll inner line (53) when the movable scroll outer line (64) and the fixed scroll inner line (53) are closest to each other. The 2 nd side gap (G2) is greater than the 1 st side gap (G1).)

1. A scroll compressor (10) having:

a fixed scroll (50) having a fixed scroll (52); and

a movable scroll (60) having a movable scroll (62),

a 1 st scroll (62) and a 2 nd scroll (52) are one and the other of the fixed scroll and the movable scroll, respectively, and a 2 nd thickness (T2) which is a thickness of the 2 nd scroll is larger than a 1 st thickness (T1) which is a thickness of the 1 st scroll,

a 1 st flank gap (G1) is a distance between the 1 st scroll inner line (63) and the 2 nd scroll outer line (54) when the 1 st scroll inner line (63) and the 2 nd scroll outer line (54) are closest to each other,

a 2 nd side gap (G2) is a distance between the outer line (64) of the 1 st scroll and the inner line (53) of the 2 nd scroll when the outer line (64) of the 1 st scroll and the inner line (53) of the 2 nd scroll are closest to each other,

the 2 nd side gap (G2) is greater than the 1 st side gap (G1).

2. The scroll compressor of claim 1,

the 2 nd thickness (T2) is 130% or more of the 1 st thickness (T1).

3. The scroll compressor according to claim 1 or 2,

the 2 nd side gap (G2) is 110% or more of the 1 st side gap (G1).

4. The scroll compressor of claim 3,

the 2 nd side gap (G2) is 120% or more of the 1 st side gap (G1).

5. The scroll compressor according to any one of claims 1 to 4, wherein,

the height (H1) of the 1 st scroll is more than 7 times of the 1 st thickness (T1).

6. The scroll compressor according to any one of claims 1 to 5, wherein,

the 2 nd scroll (52) has an inner peripheral side scroll part (521) and an outer peripheral side scroll part (522),

the 1 st scroll (62) has a reciprocating scroll portion (625) relatively reciprocating between the inner circumference side scroll portion and the outer circumference side scroll portion,

the 1 st side gap (G1) is a gap formed by the inner peripheral side scroll part (521) and the reciprocating scroll part (625),

the 2 nd side gap (G2) is a gap formed by the outer peripheral side scroll part (522) and the reciprocating scroll part (625),

the 1 st thickness (T1) is a thickness of the reciprocating scroll portion (625),

the 2 nd thickness (T2) is a thickness of the outer peripheral side scroll portion (522).

7. The scroll compressor according to any one of claims 1 to 6, wherein,

the 1 st scroll (62) is the movable scroll (62),

the 2 nd scroll (52) is the fixed scroll (52).

Technical Field

The present invention relates to a scroll compressor.

Background

In a scroll compressor, a compression chamber is defined by a fixed scroll and a movable scroll having a spiral scroll. Since each portion of the scroll is in contact with a fluid having a different pressure, the portion may be deformed by a pressure difference. In order to prevent the occurrence of such deformation and the occurrence of operational abnormality, in the scroll compressor disclosed in patent document 1 (japanese patent application laid-open No. 2015-71947), a gap between the inner side of the movable scroll and the outer side of the fixed scroll is set to be large. The premise is the following recognition: the movable scroll is inclined inward due to deformation, and easily interferes with the fixed scroll on the inner side.

Disclosure of Invention

Problems to be solved by the invention

Since the direction in which the scroll is easily tilted varies depending on various conditions, the movable scroll may be tilted outward. In this case, the structure proposed in patent document 1 is rather susceptible to deformation of the scroll, and there is a possibility that an operation abnormality such as noise may be caused by interference between the fixed scroll and the movable scroll. When a refrigerant of a type that can be heated to a high temperature is compressed, the scroll is thermally expanded, and thus an operation abnormality is more likely to occur.

The invention provides a scroll compressor which is not easy to generate abnormal operation when a scroll is deformed due to pressure difference.

Means for solving the problems

The scroll compressor according to claim 1 of the present invention includes: a fixed scroll having a fixed scroll pan; and a movable scroll having a movable scroll. The 1 st scroll and the 2 nd scroll are one and the other of the fixed scroll and the movable scroll, respectively, and the 2 nd scroll, which is the thickness of the 2 nd scroll, is larger than the 1 st scroll, which is the thickness of the 1 st scroll. The 1 st flank gap is a gap between an inner line of the 1 st scroll and an outer line of the 2 nd scroll when the inner line of the 1 st scroll and the outer line of the 2 nd scroll are closest. The 2 nd side gap is a space between the outer line of the 1 st scroll and the inner line of the 2 nd scroll when the outer line of the 1 st scroll and the inner line of the 2 nd scroll are closest. The 2 nd side gap is greater than the 1 st side gap.

According to this structure, the 2 nd flank gap on the outer line side of the 1 st scroll is larger than the 1 st flank gap on the inner line side of the 1 st scroll. Since the inner peripheral side of the scroll contains a high-pressure fluid as compared with the outer peripheral side, the 1 st scroll having a small thickness is likely to tilt outward. Therefore, the tilting amount of the 1 st scroll is accommodated in the relatively large 2 nd side surface gap, and therefore, the interference between the 1 st scroll and the 2 nd scroll is suppressed, and the operation abnormality is not easily caused.

The scroll compressor according to claim 2 of the present invention is the scroll compressor according to claim 1, wherein the 2 nd thickness is 130% or more of the 1 st thickness.

According to this structure, the 2 nd thickness is 130% or more of the 1 st thickness. The probability of the 1 st scroll plate falling is higher than that of the 2 nd scroll plate which is 30% or more thick. The tilting amount of the 1 st scroll can be accommodated in the 2 nd side surface gap. Therefore, interference is more reliably suppressed when the scroll pan is tilted.

In the scroll compressor according to claim 3 of the present invention, in the scroll compressor according to claim 1 or 2, the 2 nd side surface clearance is 110% or more of the 1 st side surface clearance.

According to this structure, the 2 nd side surface gap is 110% or more of the 1 st side surface gap. Therefore, the 2 nd flank gap can further accommodate the amount of inclination of the 1 st scroll by a difference of 10%.

The scroll compressor according to claim 4 of the present invention is the scroll compressor according to claim 3, wherein the 2 nd flank gap is 120% or more of the 1 st flank gap.

According to this structure, the 2 nd side surface gap is 120% or more of the 1 st side surface gap. Therefore, the 2 nd flank gap can further accommodate the amount of inclination of the 1 st scroll by a larger difference of 20%.

The scroll compressor according to claim 5 of the present invention is the scroll compressor according to any one of claims 1 to 4, wherein the height of the 1 st scroll is 7 times or more the 1 st thickness.

According to this structure, the height of the 1 st scroll is 7 times or more the thickness. The scroll having a larger ratio of height to thickness is more likely to fall due to a pressure difference of fluid. Therefore, in the structure in which the inclination of the scroll scrolls is easily caused, the interference between the scroll scrolls is more reliably suppressed.

A scroll compressor according to claim 6 of the present invention is the scroll compressor according to any one of claims 1 to 5, wherein the 2 nd scroll has an inner peripheral side scroll part and an outer peripheral side scroll part. The 1 st scroll has a reciprocating scroll portion that relatively reciprocates between an inner peripheral side scroll portion and an outer peripheral side scroll portion. The 1 st side gap is a gap formed by the inner peripheral side scroll portion and the reciprocating scroll portion. The 2 nd side gap is a gap formed between the outer peripheral scroll portion and the reciprocating scroll portion. The 1 st thickness is a thickness of the reciprocating scroll portion. The 2 nd thickness is the thickness of the outer peripheral side scroll portion.

According to this structure, the reciprocating scroll portion of the 1 st scroll is sandwiched by the inner circumference side scroll portion and the outer circumference side scroll portion of the 2 nd scroll. The 1 st side gap is formed by the reciprocating scroll portion and the inner peripheral side scroll portion. The 2 nd side gap is formed by the reciprocating scroll portion and the outer peripheral side scroll portion. Therefore, when the thicknesses of the 1 st scroll and the 2 nd scroll differ depending on the location, it is possible to determine which of the 1 st thickness, the 2 nd thickness, the 1 st flank gap, and the 2 nd flank gap should be obtained depending on which portion of the scroll.

A scroll compressor according to claim 7 of the present invention is the scroll compressor according to any one of claims 1 to 6, wherein the 1 st scroll is a movable scroll, and the 2 nd scroll is a fixed scroll.

According to this structure, the 1 st scroll is a movable scroll, and therefore, the movable scroll has a small thickness and is light in weight. Therefore, the rotational driving force for revolving the movable scroll is only required to be small, and therefore, the energy efficiency of the scroll compressor can be easily improved.

Effects of the invention

According to the scroll compressor of the present invention, interference is suppressed when the scroll pan is tilted, and an operation abnormality is not easily caused.

Drawings

Fig. 1 is a sectional view of a scroll compressor 10 according to an embodiment of the present invention.

Fig. 2 is a sectional view of the fixed scroll 50 of the compression mechanism 40.

Fig. 3 is a sectional view of the movable scroll 60 of the compression mechanism 40.

Fig. 4 is a sectional view of the compression mechanism 40 along the horizontal plane.

Fig. 5 is a schematic diagram showing a cross section of the compression mechanism 40.

Fig. 6 is a schematic diagram showing a cross section of the compression mechanism 40.

Description of the reference symbols

10 scroll compressor

20 outer casing

30 motor

40 compression mechanism

50 fixed scroll

51 fixed scroll end plate

52 fixed scroll

53 fixed scroll inner line

54 fixed scroll outer line

60 Movable scroll

61 Movable scroll end plate

62 Movable scroll

63 inner line of movable scroll

64 movable scroll outer line

Detailed Description

(1) Integral structure

FIG. 1 illustrates a scroll compressor 10 according to one embodiment of the present invention. The scroll compressor 10 is mounted on an air conditioner or the like, and compresses a refrigerant as a fluid. The scroll compressor 10 has a housing 20, a motor 30, a crankshaft 35, a compression mechanism 40, and frame members 70, 75.

The refrigerant to be compressed in the scroll compressor 10 is, for example, a refrigerant that is relatively likely to have a high temperature and a high pressure around the fixed scroll 50 and the movable scroll 60 of the compression mechanism 40. In other words, the refrigerant to be compressed in the scroll compressor 10 is a refrigerant having a relatively high condensing pressure. Specifically, the refrigerant to be compressed by the scroll compressor 10 is, for example, R32(R32 alone), a mixed refrigerant containing 50% or more of R32 (for example, R410A, R452B, R454B, and the like), a mixed refrigerant of R1123 and R32, or the like. In addition, in particular, the refrigerant to be compressed in the scroll compressor 10 here is a refrigerant having a higher condensation pressure ratio than R410A, such as a mixed refrigerant of R32, R1123, and R32. However, the refrigerant to be compressed in the scroll compressor 10 is not limited to the above refrigerant.

(2) Detailed structure

(2-1) case 20

The casing 20 houses various components of the scroll compressor 10 and the refrigerant. The housing 20 is able to withstand the high pressure of the refrigerant. The housing 20 has a body portion 21, an upper portion 22, and a lower portion 23 joined to each other. The upper portion 22 is provided with a suction pipe 15 for sucking a low-pressure gas refrigerant. The main body 21 is provided with a discharge pipe 16 for discharging a high-pressure gas refrigerant. A lower portion of the housing 20 is filled with a lubricant L for lubricating a sliding portion among various components.

(2-2) Motor 30

The motor 30 is supplied with electric power to generate power for compressing the refrigerant. The motor 30 has a stator 31 and a rotor 32. The stator 31 is fixed to the body portion 21 of the housing 20. The stator 31 has windings not shown. The winding receives electric power to generate an alternating magnetic field. The rotor 32 is rotatably disposed in a central cavity of the stator 31. A permanent magnet, not shown, is embedded in the rotor 32. The permanent magnets receive a force from the alternating magnetic field, and thereby the rotor 32 rotates, generating power.

(2-3) crankshaft 35

The crankshaft 35 serves to transmit power generated by the motor 30 to the compression mechanism 40. The crankshaft 35 has a main shaft portion 36 and an eccentric portion 37. The main shaft portion 36 is fixed so as to penetrate the rotor 32 and is concentric with the rotor 32. The eccentric portion 37 is eccentric with respect to the rotor 32 and is connected to the compression mechanism 40.

(2-4) compression mechanism 40

The compression mechanism 40 compresses a low-pressure gas refrigerant to generate a high-pressure gas refrigerant. The compression mechanism 40 has a fixed scroll 50 and a movable scroll 60. The fixed scroll 50 is fixed directly or indirectly to the housing 20. The movable scroll 60 is connected to the eccentric portion 37 of the crankshaft 35 and can orbit with respect to the fixed scroll 50. The fixed scroll 50 and the movable scroll 60 define the compression chamber 41. The volume of the compression chamber 41 is changed by the revolution of the movable scroll 60, whereby the low-pressure gas refrigerant is compressed to become a high-pressure gas refrigerant. The high-pressure gas refrigerant is discharged from the discharge port 42 to the outside of the compression mechanism 40.

(2-5) frame Member 70, 75

The frame members 70 and 75 rotatably support the crankshaft 35. A frame member 70 supports the upper portion of the main shaft portion 36. The other frame member 75 supports the lower side of the main shaft portion 36. The frame members 70, 75 are secured directly or indirectly to the housing 20.

(3) Operation of scroll compressor 10

The rotor 32 of the motor 30 shown in fig. 1 is rotated by electric power supplied from the outside. The rotation of rotor 32 is transmitted to main shaft 36 of crankshaft 35. The movable scroll 60 orbits relative to the fixed scroll 50 by power transmitted from the eccentric portion 37 of the crankshaft 35. The low-pressure gas refrigerant taken in from the intake pipe 15 enters the compression chamber 41 on the outer peripheral side of the compression mechanism 40. The compression chamber 41 moves toward the center of the compression mechanism 40 while decreasing in volume by the orbital motion of the movable scroll 60. In this process, the low-pressure gas refrigerant is compressed to become a high-pressure gas refrigerant. The high-pressure gas refrigerant is discharged from the discharge port 42 to the outside of the compression mechanism 40, and moves to the casing internal space. Then, the high-pressure gas refrigerant is discharged from the discharge pipe 16 to the outside of the casing 20.

(4) Detailed structure of the compression mechanism 40

Fig. 2 shows the fixed scroll 50. The fixed scroll 50 has a fixed scroll end plate 51 and a fixed scroll 52 standing on the fixed scroll end plate 51. The fixed scroll 52 is of a spiral shape, for example, having an involute curve shape.

Fig. 3 shows the movable scroll 60. The movable scroll 60 includes a movable scroll end plate 61 and a movable scroll 62 standing on the movable scroll end plate 61. The movable scroll 62 is of a spiral shape, for example, having an involute curve shape.

Fig. 4 is a sectional view in the horizontal plane of the compression mechanism 40. The fixed scroll 52 and the movable scroll 62 approach each other at a plurality of locations. These adjacent portions are blocked by lubricating oil or the like to form seal points. Thereby, a plurality of compression chambers 41 separated from each other are defined. The fixed scroll 52 has a fixed scroll inner line 53 as a center side and a fixed scroll outer line 54 as an outer peripheral side. The movable scroll 62 has a center side movable scroll inner line 63 and an outer peripheral side movable scroll outer line 64.

The movable scroll 62 is disposed between adjacent 2 portions of the fixed scroll 52. That is, when any portion of the movable scroll 62 is referred to as a reciprocating scroll portion 625, the reciprocating scroll portion 625 is disposed between the inner circumference side scroll portion 521 and the outer circumference side scroll portion 522 of the fixed scroll 52. By the orbiting of the movable scroll 60, the reciprocating scroll portion 625 reciprocates between the inner circumferential scroll portion 521 and the outer circumferential scroll portion 522.

Fig. 5 and 6 show the inner and outer circumferential scroll portions 521 and 522 of the fixed scroll 52 and the reciprocating scroll portion 625 of the movable scroll 62. The inner peripheral side scroll portion 521 is located on the center side C of the compression mechanism 40. Outer peripheral scroll portion 522 is located on outer peripheral side P of compression mechanism 40. Reciprocating scroll portion 625 is located between inner circumference side scroll portion 521 and outer circumference side scroll portion 522. Here, the thickness of the reciprocating scroll portion 625 is referred to as a 1 st thickness T1, and the thickness of the outer peripheral scroll portion 522 is referred to as a 2 nd thickness T2. Further, the height of the movable scroll 62 is referred to as a 1 st height H1.

Fig. 5 shows reciprocating scroll portion 625 closest to inner peripheral side scroll portion 521. The gap formed by inner circumferential scroll portion 521 and reciprocating scroll portion 625 at this time is referred to as 1 st side gap G1. The 1 st flank gap G1 is formed by the movable scroll inner line 63 and the fixed scroll outer line 54.

Fig. 6 shows a state where reciprocating scroll portion 625 is closest to outer peripheral side scroll portion 522. The gap formed by outer peripheral scroll portion 522 and reciprocating scroll portion 625 at this time is referred to as 2 nd side gap G2. The 2 nd side gap G2 is formed by the movable scroll outer line 64 and the fixed scroll inner line 53.

In the compression mechanism 40 of the scroll compressor 10 according to the present embodiment, the dimensions are set as follows.

The 2 nd side gap G2 is set to be larger than the 1 st side gap G1. Specifically, the 2 nd side gap G2 is 110% or more, preferably 120% or more of the 1 st side gap G1. Further, the 2 nd side gap G2 may be set to 1000% or less, preferably 500% or less of the 1 st side gap G1.

The 2 nd thickness T2 is set to 130% or more of the 1 st thickness T1. Further, the 2 nd thickness T2 may be set to 1000% or less, preferably 500% or less of the 1 st thickness T1.

The 1 st height H1 is set to be 7 times or more of the 1 st thickness T1. Further, the 1 st height H1 may be set to be 100 times or less, preferably 50 times or less, of the 1 st thickness T1.

(5) Feature(s)

(5-1)

The 2 nd side gap G2 on the movable scroll outer line 64 side is larger than the 1 st side gap G1 on the movable scroll inner line 63 side. Since the center side C of the compression mechanism 40 contains a high-pressure fluid as compared with the outer peripheral side P, the reciprocating scroll portion 625 of the movable scroll 62 having a small thickness such as the 1 st thickness T1 is likely to tilt outward. Therefore, the amount of inclination of the reciprocating scroll portion 625 is accommodated in the relatively large 2 nd side gap G2, and therefore, interference between the movable scroll 62 and the fixed scroll 52 is suppressed, and an operation abnormality is not easily caused.

(5-2)

The 2 nd thickness T2 is 130% or more of the 1 st thickness T1. The movable scroll 62 has a higher probability of falling down than the fixed scroll 52 having a thickness of 30% or more. The amount of inclination of the movable scroll 62 can be accommodated in the 2 nd side gap G2. Therefore, interference is more reliably suppressed when the movable scroll 62 is tilted.

(5-3)

The 2 nd side gap G2 is 110% or more, preferably 120% or more of the 1 st side gap G1. Therefore, the 2 nd side gap can further accommodate the amount of inclination of the movable scroll 62 by a difference of 10% or 20%.

(5-4)

The height of the movable scroll 62, i.e., the 1 st height H1, is 7 times or more the thickness of the movable scroll 62, i.e., the 1 st thickness T1. The scroll having a larger ratio of height to thickness is more likely to fall due to a pressure difference of fluid. Therefore, in the structure in which the inclination of the movable scroll 62 is easily caused, the interference of the movable scroll 62 and the fixed scroll 52 is more reliably suppressed.

(5-5)

The reciprocating scroll portion 625 of the movable scroll 62 is sandwiched between the inner circumferential scroll portion 521 and the outer circumferential scroll portion 522 of the fixed scroll 52. A 1 st side gap G1 is formed by reciprocating scroll portion 625 and inner peripheral side scroll portion 521. A 2 nd side gap G2 is formed by reciprocating scroll portion 625 and outer peripheral side scroll portion 522. Therefore, when the thicknesses of the movable scroll 62 and the fixed scroll 52 differ from place to place, it is possible to determine at which portion of the scroll the 1 st thickness T1, the 2 nd thickness T2, the 1 st side gap G1, and the 2 nd side gap G2 should be obtained.

(5-6)

The movable scroll 62 of the movable member, i.e., the movable scroll 60, has a small thickness, i.e., the 1 st thickness T1, and thus is light in weight. Therefore, the rotational driving force for revolving the movable scroll 60 is only required to be small, and therefore, the energy efficiency of the scroll compressor 10 is easily improved.

(6) Modification example

Next, a modification of the present embodiment will be described. In addition, a plurality of modifications may be appropriately combined.

(6-1) modification A

In the above embodiment, the 1 st thickness T1 is set as the thickness of the reciprocating scroll portion 625, and the 2 nd thickness T2 is set as the thickness of the outer peripheral side scroll portion 522. Alternatively, it is also possible to set 1 st thickness T1 to the thickness of reciprocating scroll portion 625 and set 2 nd thickness T2 to the thickness of inner peripheral side scroll portion 521 rather than outer peripheral side scroll portion 522, and then apply the already described ratio of 1 st thickness T1 to 2 nd thickness T2.

With this configuration, interference between the movable scroll 62 and the fixed scroll 52 is suppressed, and design constraints can be changed.

(6-2) modification B

The fixed scroll 50 and the movable scroll 60 may be exchanged for the various dimensional conditions described in the above embodiments. That is, the orbiting scroll part 625, the 1 st thickness T1, and the 1 st height H1 may be referred to as the fixed scroll 50, and the inner circumference side scroll part 521, the outer circumference side scroll part 522, and the 2 nd thickness T2 may be referred to as the movable scroll 60. Then, the size relationship of the 1 st side gap G1 and the 2 nd side gap G2, the ratio of the 1 st thickness T1 and the 2 nd thickness T2, and other various dimensional conditions are applied.

According to this structure, the fixed scroll 52 has a small thickness, i.e., the 1 st thickness T1, and therefore, the fixed scroll 52 is more easily tilted. Under such conditions, an effect of suppressing interference between the movable scroll 62 and the fixed scroll 52 can be obtained.