CN110621879A

CN110621879A - Scroll fluid machine

Info

Publication number: CN110621879A
Application number: CN201780090292.4A
Authority: CN
Inventors: 小林义雄; 坂本晋; 渡边翔
Original assignee: Hitachi Production Machine System
Current assignee: Hitachi Production Machine System; Hitachi Industrial Equipment Systems Co Ltd
Priority date: 2017-05-15
Filing date: 2017-05-15
Publication date: 2019-12-27
Anticipated expiration: 2037-05-15
Also published as: WO2018211567A1; JPWO2018211567A1; CN110621879B; JP6792072B2

Abstract

The invention provides a scroll fluid machine which can reduce damage of a scroll wrap and the like caused by movement of a base plate and can realize long service life. The scroll fluid machine of the present invention includes: a fixed scroll having a spiral wrap portion on a tooth bottom surface of an end plate; and an orbiting scroll provided to face the fixed scroll, the orbiting scroll having a spiral wrap portion provided on a tooth bottom surface of an end plate, a plurality of compression chambers are formed between the lap and the lap of the fixed scroll, a groove extending along a tooth crest of the lap is formed on at least one lap of the orbiting scroll and the fixed scroll, a seal member which is in sliding contact with a bottom land of the scroll member facing the recess is mounted in the recess, and a wear-resistant plate-like member is disposed on the bottom land facing the seal member, the plate-like member and the spiral wrap portion on which the plate-like member is disposed have a predetermined gap in a winding direction of a spiral, the inner line side or the outer line side of the spiral wrap of the scroll contacts with the side surface of the plate-like member and stops rotating, so that the plate-like member does not contact the spiral wrap portion in the winding direction of the spiral.

Description

Scroll fluid machine

Technical Field

The present invention relates to a scroll-type fluid machine suitable for use in, for example, an air compressor and a vacuum pump.

Background

Patent document 1 describes "a scroll compressor including: a fixed scroll member for fixing the scroll wrap is provided upright on one surface of the fixed end plate; an orbiting scroll member in which an orbiting scroll wrap is erected on one surface of an orbiting end plate, and which is combined to form a compression chamber so as to be rotationally driven while being prevented from rotating on its axis with respect to the fixed scroll member; and a sheet seal member fitted into a sheet seal groove provided in a tip end surface of each of the fixed scroll wrap and the orbiting scroll wrap, wherein a bottom plate in sliding contact with the sheet seal member is provided on a tooth bottom surface of the scroll wrap of either or both of the fixed scroll wrap and the orbiting scroll wrap in the scroll compressor, and a support member having a lower melting point than the sheet seal member is provided on a back surface side of the bottom plate. "(claim 6).

Patent document 2 discloses "a scroll fluid machine in which a fixed scroll and a movable scroll, each having a wrap formed of a spiral curve formed integrally with a first end plate, are caused to mesh with each other so that the wrap is inside and the movable scroll is caused to orbit with respect to the fixed scroll, wherein a through hole having a spiral curve formed in the same shape as the wrap of the two scrolls or one of the scrolls is provided, a second end plate formed of a metallic rigid body having a higher surface accuracy than the first end plate is disposed on the first end plate, and the chamfer of the corner of the second end plate surface on the side in contact with the first end plate is larger than the chamfer of the corner of the opposing surface of the opposing wrap. "(scope of claims).

Documents of the prior art

Patent document 1: japanese patent laid-open No. 2008-163896

Patent document 2: japanese laid-open patent publication No. 2-70988

Disclosure of Invention

Technical problem to be solved by the invention

Patent documents 1 and 2 describe scroll compressors in which a bottom plate to which a sheet-like seal member is brought into sliding contact is provided on a tooth bottom surface of a spiral wrap of either or both of a fixed scroll and an orbiting scroll. However, in patent document 1 or patent document 2, it is not considered that the spiral wrap and the sheet seal member are damaged by the movement of the base plate.

Accordingly, an object of the present invention is to provide a scroll-type fluid machine capable of reducing damage to a spiral wrap or the like caused by movement of a base plate and achieving a longer service life.

Means for solving the problems

An example of a scroll fluid machine according to the present invention for solving the above-described problems is a scroll fluid machine including: a fixed scroll having a spiral wrap portion on a tooth bottom surface of an end plate; and an orbiting scroll provided to face the fixed scroll, the orbiting scroll having a spiral wrap portion provided on a tooth bottom surface of an end plate, a plurality of compression chambers are formed between the lap and the lap of the fixed scroll, a groove extending along a tooth crest of the lap is formed on at least one lap of the orbiting scroll and the fixed scroll, a seal member which is in sliding contact with a bottom land of the scroll member facing the recess is mounted in the recess, and a wear-resistant plate-like member is disposed on the bottom land facing the seal member, the plate-like member and the spiral wrap portion on which the plate-like member is disposed have a predetermined gap in a winding direction of a spiral, the inner line side or the outer line side of the spiral wrap of the scroll contacts with the side surface of the plate-like member and stops rotating, so that the plate-like member does not contact the spiral wrap portion in the winding direction of the spiral.

Another example of a scroll fluid machine according to the present invention is a scroll fluid machine including: a fixed scroll having a spiral wrap portion on a tooth bottom surface of an end plate; and an orbiting scroll disposed to face the fixed scroll, wherein a spiral wrap is provided on a land of an end plate, a plurality of compression chambers are formed between the wrap and the wrap of the fixed scroll, a groove extending along a tooth crest of the wrap is formed in at least one of the orbiting scroll and the wrap of the fixed scroll, a seal member slidably contacting the land of the facing scroll is mounted in the groove, and a wear-resistant plate-like member is disposed on the land facing the seal member, and the plate-like member is fixed to the fixed scroll or the orbiting scroll by a screw.

Effects of the invention

According to the present invention, damage to a spiral wrap or the like caused by movement of a base plate can be reduced in a scroll fluid machine, and a longer life can be achieved.

Drawings

Fig. 1 is a longitudinal sectional view showing a scroll air compressor according to embodiment 1 of the present invention.

Fig. 2 is a developed perspective view showing a scroll type air compressor according to embodiment 1 of the present invention.

Fig. 3 is a partial enlarged view of the vicinity of the leaf seal of fig. 1.

Fig. 4 is a view showing the sheet-like sealing member of fig. 3.

Fig. 5 is a partial enlarged view in the Y-Y direction of fig. 1.

Fig. 6 is a cross-sectional view in the Y-Y direction of fig. 1.

Fig. 7 is a diagram showing the relationship between the base plate and the wrap when the orbiting scroll of embodiment 1 rotates forward.

Fig. 8 is a diagram showing the relationship between the base plate and the wrap when the orbiting scroll of embodiment 1 is reversed.

Fig. 9 is a diagram showing the fixing position of the base plate in embodiment 2 of the present invention.

Fig. 10 is a diagram showing another fixing position of the base plate in embodiment 2 of the present invention.

Fig. 11 is a diagram showing a positional relationship between the bottom plate and the sheet-like sealing member.

Fig. 12 is a diagram showing a positional relationship between the bottom plate and the sheet-like sealing member in example 3.

Fig. 13 is a diagram showing another positional relationship between the bottom plate and the sheet-like sealing member for comparison.

Fig. 14 is a developed perspective view showing a scroll type air compressor according to embodiment 4 of the present invention.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same reference numerals are assigned to the components common to the respective drawings as much as possible, and redundant description thereof will be omitted.

Example 1

A scroll-type fluid machine according to embodiment 1 of the present invention will be described with reference to fig. 1 to 8, taking a case of being used as an air compressor as an example.

Fig. 1 is a longitudinal sectional view of a scroll air compressor according to embodiment 1 of the present invention. Fig. 2 is a developed perspective view of the scroll air compressor. In the drawings, reference numeral 1 denotes a fixed scroll which constitutes a part of a housing of a scroll type air compressor, and the fixed scroll 1 is fastened to an opening end side of a housing main body 47 (fig. 2) formed in a substantially tubular shape so as to be capped at the opening end side. The fixed scroll 1 is made of, for example, an aluminum alloy or the like, and is configured by a disc-shaped end plate 2 whose center is arranged to coincide with an axis O1-O1 of a drive shaft 17 to be described later, a spiral wrap 3 erected on a tooth bottom surface 2A of the end plate 2, and a support portion 4 located on an outer peripheral side of the end plate 2 and formed in a cylindrical shape so as to surround the wrap 3.

As shown in fig. 5, the lap 3 of the fixed scroll 1 has an inner peripheral side serving as a winding start end and an outer peripheral side (not shown) serving as a winding end, and is formed into a spiral shape of, for example, about 3 lap halves. As shown in fig. 3, the tooth crest 3A of the lap 3 is spaced apart from the tooth bottom 10A of the orbiting scroll 9, which will be described later, by a small clearance C.

Reference numeral 5 denotes a groove formed on the tooth crest 3A side of the lap 3, and as shown in fig. 3, the groove is formed so as to have a cross section of コ at the middle portion in the width direction on the tooth crest 3A side of the lap 3, and the bottom surface 5A and the left and right side surfaces 5B, 5C of the groove 5 extend from the winding start end to the winding end along the spiral shape of the lap 3. A sheet seal 6, which will be described later, is fitted in the recess 5 to seal the space between the recess and a bottom plate 10B, and the bottom plate 10B is provided between the bottom plate and a tooth bottom 10A of the orbiting scroll 9.

Reference numeral 6 denotes a sheet seal as a seal member which is mounted in the recessed groove 5 of the winding barrel 3, and the sheet seal 6 is formed as a long sheet seal having a rectangular cross section formed of, for example, an elastic resin material, and extends spirally along the longitudinal direction of the recessed groove 5, as shown in fig. 4.

As shown in fig. 3, the sheet seal 6 includes a lower surface 6A as a pressure receiving surface which abuts against the bottom surface 5A of the concave groove 5, an upper surface 6B which faces the lower surface 6A in the vertical direction and is in sliding contact with the other bottom plate 10B, and an inner surface 6C and an outer surface 6D which are positioned radially inside and outside the sheet seal 6 formed in a spiral shape, and lower and inner lips 7 and 8 which will be described later are integrally formed on the lower and inner surfaces 6A and 6C, respectively. The sheet seal 6 is inserted into the recess 5 with a slight gap between the inner and outer surfaces 6C and 6D so that the lower surface 6A is in contact with the bottom surface 5A of the recess 5, and is allowed to float from the bottom surface 5A of the recess 5 toward the bottom plate 10B of the orbiting scroll 9 as the other.

Reference numerals 7, and … denote lower lips as bottom lips formed at predetermined intervals in the longitudinal direction on the lower surface 6A of the sheet seal 6, and the lower lips 7 are formed integrally by obliquely cutting the lower surface 6A of the sheet seal 6 at predetermined intervals as shown in fig. 4, and the tip side thereof is a free end and extends from the lower surface 6A.

Reference numerals 8, and … denote inner lips as side lips of the sheet seal 6, and each of the inner lips 8 is formed substantially in the same manner as the lower lip 7, and is formed by obliquely cutting into the inner surface 6C of the sheet seal 6 at a predetermined interval as shown in fig. 4, and the tip side thereof is a free end and extends from the inner surface 6C.

In fig. 1, reference numeral 9 denotes an orbiting scroll which is provided to face a fixed scroll 1 and to be rotatable in the housing main body, and the orbiting scroll 9 is made of, for example, an aluminum alloy or the like, and is configured by an end plate 10 which is formed into a disc shape with a bottom land 10A on the front surface side, a lap 11 which is erected from the bottom land 10A of the end plate 10 toward an end plate 2 of the fixed scroll 1 and is formed into a spiral shape similarly to the lap 3 of the fixed scroll 1, and a boss portion 12 which is provided at the center of the back surface of the end plate 10, and the boss portion 12 is rotatably attached to a crankshaft of a drive shaft 17 which will be described later.

Here, the lap 11 of the orbiting scroll 9 is formed into a spiral shape of, for example, about 3-half lap as in the lap 3 of the fixed scroll 1, and as shown in fig. 3, a groove 13 is formed from a bottom surface 13A and left and right side surfaces 13B and 13C on the tooth crest 11A side thereof, and the groove 13 is formed into a cross-sectional shape of コ.

Reference numeral 14 denotes another sheet seal as a seal member formed in the same manner as the sheet seal 6 on the fixed scroll 1 side, and the sheet seal 14 is attached to the concave groove 13 and is configured by a lower side surface 14A abutting on the bottom surface 13A thereof, an upper side surface 14B sliding-contacting with the bottom plate 2B configured between the other tooth bottom surface 2A, an inner side surface 14C, and an outer side surface 14D. Further, similarly to the sheet seal 6, lower lips 15 and inner lips 16 are integrally formed on the lower surface 14A and the inner surface 14C of the sheet seal 14, respectively.

In the present embodiment, the grooves 5 and 13 and the sheet seals 6 and 14 are provided in both the fixed scroll 1 and the orbiting scroll 9, but may be provided in only one of them.

Reference numeral 17 denotes a drive shaft rotatably provided in the housing main body, the drive shaft 17 is a crankshaft whose tip end extends into the housing main body, and an axis O2-O2 of the crankshaft is eccentric by a predetermined dimension δ from an axis O1-O1 of the drive shaft 17. A boss portion 12 of the orbiting scroll 9 is rotatably attached to the inside of the crankshaft of the drive shaft 17 via a orbiting bearing 18, and orbiting motion is imparted to the orbiting scroll 9 via a rotation preventing mechanism (not shown) or the like.

Here, the wrap 11 of the orbiting scroll 9 is arranged to overlap the wrap 3 of the fixed scroll 1 while being offset by a predetermined angle in the circumferential direction, and as shown in fig. 5, a plurality of crescent-shaped compression chambers R, R, … are defined between the wraps 3, 11. When the orbiting scroll 9 is made to orbit with respect to the fixed scroll 1, the volume of each compression chamber R is continuously reduced, and the air sucked from the suction port 19 described later is sequentially compressed.

19. A suction port and a discharge port formed in the fixed scroll 1 are denoted by 20, the suction port 19 is bored in the outer peripheral side of the end plate 2 so as to communicate with the outermost compression chamber R, and the discharge port 20 is bored in the central portion of the end plate 2 so as to communicate with the innermost compression chamber R.

The scroll type air compressor has the above-described configuration, and the operation thereof will be described below.

First, when the drive shaft 17 is rotationally driven from the outside of the casing by a drive source (not shown) such as a motor, the rotation is transmitted from the crankshaft of the drive shaft 17 to the orbiting scroll 9 via the orbiting bearing 18, and the orbiting scroll 9 performs a rotational motion with a radius of rotation of a size δ about the axis O1-O1 of the drive shaft 17.

By this rotational movement, the compression chambers R partitioned between the respective winding units 3 and 11 are continuously narrowed toward the center, and the air sucked through the suction port 19 is sequentially compressed and discharged from the discharge port 20 to an external air tank (not shown) or the like. Here, when the compression operation is started, a part of the compressed air enters the concave groove 5(13) of the winding barrel 3(11) from the compression chamber R on the high pressure side in the direction a indicated by the arrow shown in fig. 3, and the sheet seal 6(14) receives the pressure of the compressed air on the lower surface 6A (14A) serving as the pressure receiving surface, floats from the concave groove 5(13), and is pressed against the bottom plate 10B formed between the tooth bottom surface 10A (2A) of the opposite end plate 10 (2). Thereby, the upper side 6B (14B) of the sheet seal 6(14) is in sliding contact with the other bottom plate 10B (2B), and the compression chambers R partitioned between the winding body portions 3 and 11 are hermetically sealed.

In addition, the lower lips 7 and 15 are configured such that the tip end sides of the lower lips 7 and 15 are pressed against the bottom surfaces 5A (13A) of the pockets 5 and 13 by compressed air entering the pockets 5 and 13 from the compression chamber R on the inner circumferential side to the compression chamber R on the outer circumferential side in the compression chambers R in the direction B indicated by the arrow in fig. 5, and the spaces between the bottom surfaces 5A (13A) of the pockets 5 and 13 and the sheet-like seals 6 and 14 are hermetically sealed.

In addition, similarly to the above, the tip end side of each inner lip 8(16) is pressed against the one side surface 5B (13B) of the groove 5(13) by the compressed air entering the groove 5(13) and the inner lip 8(16), and the side surface 5B (13B) of the groove 5(13) and the sheet-like seal 6(14) are hermetically sealed, and the outer side surface 6D (14D) of the sheet-like seal 6(14) is pressed against the other side surface 5C (13C) to hermetically seal therebetween.

However, in the above scroll-type air compressor, when the orbiting scroll 9 is made to orbit with respect to the fixed scroll 1, each compression chamber R is in a high temperature state, and particularly, the compression chamber R on the inner peripheral side (the discharge port 20 side) is in a high temperature and high pressure state. Therefore, the stationary scroll 1 and the orbiting scroll 9 that define the compression chambers R need to have improved wear resistance and corrosion resistance of the surfaces of the tooth bottoms 2A and 10A.

Therefore, in the present embodiment, as shown in fig. 2, the bottom plate 10B is disposed between the spiral wrap 11 provided on the orbiting scroll 9. Similarly, a bottom plate 2B is disposed between the spiral wrap portions 3 of the fixed scroll 1. The bottom plates 2B and 10B are made of wear-resistant plate members, for example, stainless steel plates.

Fig. 6 shows a bottom plate 10B provided on the orbiting scroll 9 side and a spiral wrap 11. The bottom plate 10B includes a spiral hole 10C into which the spiral wrap 11 is inserted, and the spiral wrap 11 and a side surface of the hole 10C of the bottom plate 10B have a substantially constant radial gap over substantially the entire circumference. In the winding end portion of the lap portion 11, a large gap δ e is provided in the winding direction of the scroll. Here, the clearance δ E is a distance between the winding end portion 11E of the lap 11 and the end 10E of the spiral hole 10C. Similarly, the winding start portion of the lap 11 has a gap in the winding direction of the scroll.

When the compressor is operated and the orbiting scroll 9 orbits, the base plate 10B (2B) is pressed by the leaf seal 6(14), and the orbiting scroll 9 receives a rotational force due to a frictional force with the leaf seal 6(14) by the orbiting motion. Further, the base plate 10B on the orbiting scroll side receives centrifugal force from the root of the scroll lap 11 because centrifugal force is generated by the orbiting motion of the orbiting scroll 9.

In order to improve assemblability, the scroll lap 11(3) and the bottom plate 10B (2B) are formed with a predetermined radial gap, and when the bottom plate 10B (2B) moves in the orbiting direction in the gap, a large winding direction gap (δ e) of the winding end portion needs to be secured particularly in the bottom plate 10B formed on the side of the bottom land 10A of the orbiting scroll 9. When the clearance δ E is small, the winding end portion of the hole 10C of the bottom plate 10B contacts and slides only with the winding end portion 11E of the scroll lap 11, and therefore the surface pressure is significantly increased, and the tooth root of the scroll lap winding end 11E or the end 10E of the hole 10C of the bottom plate 10B may be worn greatly.

On the other hand, when the winding direction gap δ E with the end 10E of the hole 10C of the bottom plate 10B is secured with respect to the scroll winding end 11E, the inner line 11A of the entire circumference of the lap of the orbiting scroll 9 is in contact with the side surface of the bottom plate 10B, not the winding end portion, and therefore, the contact surface pressure is suppressed, the abrasion can be prevented, and the reliability can be improved.

The relationship will be described with reference to fig. 7 and 8. Fig. 7 shows a state of forward rotation when the scroll air compressor is normally operated. Fig. 7(a) is an overall view, fig. 7(b) is an enlarged view showing a winding end portion, and fig. 7(c) is an enlarged view showing a winding start portion. When the compressor is rotated in the normal direction, the base plate 10B is rotated in the arrow direction by the rotation of the orbiting scroll, and as shown in the drawing, the base plate 10B moves outward, the inner wire 11A of the wrap 11 and the side surface of the base plate 10B are brought into large contact, and the rotation of the base plate is stopped. As shown in fig. 7(B), by securing a large winding direction gap δ E of the winding end portion of the roll body portion 11, the rotation of the bottom plate 10B can be stopped before the end portion 11E of the roll body comes into contact with the end 10E of the hole of the bottom plate. In the winding start portion, as shown in fig. 7(c), the end of the bottom plate rotates in a direction away from the end of the winding barrel 11 at the time of normal rotation, and therefore, both do not come into contact with each other.

Fig. 8 shows a state in which the scroll air compressor is rotated in a reverse direction. The reverse rotation is a case where the air pressure of a discharge pipe or the like is applied to the compressor and reversed after the compressor is stopped. Fig. 8(a) is an overall view, fig. 8(b) is an enlarged view showing a winding end portion, and fig. 8(c) is an enlarged view showing a winding start portion. When the compressor is reversed, the base plate is turned in the arrow direction by the orbiting motion of the orbiting scroll, and as shown in the drawing, the base plate 10B moves inward, the outer line 11B of the lap 11 is brought into contact with the side surface of the base plate 10B to a large extent, and the turning of the base plate 10B is stopped. At the winding end portion, as shown in fig. 8(b), the end 10E of the hole of the bottom plate is rotated in a direction away from the end 11E of the winding barrel portion 11, and therefore, both do not come into contact. By securing a large winding-direction gap in the winding start portion, the rotation of the base plate can be stopped before the end portion of the roll body comes into contact with the end of the hole of the base plate.

According to the present embodiment, compared to the case where the bottom plate rotates and the side surface of the hole of the bottom plate is brought into contact with the inner line or the outer line of the wrap to stop the rotation, the winding direction gap of the winding end portion of the wrap 11 or the winding direction gap of the winding start portion of the wrap is secured to be large, so that the wear of the scroll root or the bottom plate can be prevented, and the reliability can be improved.

Although the bottom plate 10B has been described above, the bottom plate 2B may be subjected to a rotational force, and a similar effect can be expected by securing a large winding direction gap at the winding start portion of the winding barrel portion 3, for example.

Example 2

Embodiment 2 is an example in which the base plate 10B or 2B is fixed to the orbiting scroll or the fixed scroll by a fixing screw in a non-rotating manner.

Fig. 9 shows a scroll type air compressor of embodiment 2. Fig. 9(a) shows a base plate 2B attached to the fixed scroll 1, and fig. 9(B) shows a base plate 10B attached to the orbiting scroll 9.

As shown in fig. 9(a), the base plate 2B is fixed to the fixed scroll 1 by a fixing screw 31. The portion fixed by the screw is sucked into the room, that is, a dust seal for preventing dust from entering from the outside. In order to prevent the lap 11 of the orbiting scroll 9 from coming into contact with the fixing screw 31, it is assumed that the lap 11 does not pass through. As shown in the drawing, it is preferable to set the vicinity of the winding end of the inner wire of the fixed-side winding body portion 3.

As shown in fig. 9(B), the base plate 10B is fixed to the orbiting scroll 9 by a fixing screw 32. Similarly, the portion fixed by the fixing screw 32 is the suction chamber. In order to prevent the lap 3 of the fixed scroll 1 from coming into contact with the fixing screw 32, the lap 3 is not passed. As in the fixed scroll 1, it is preferable to set the vicinity of the winding end of the inner line of the fixed-side lap 3 as illustrated.

Fig. 10 shows another example of the scroll-type air compressor according to embodiment 2. Fig. 10(a) shows a bottom plate 10B attached to the orbiting scroll 9, and fig. 10(B) shows an enlarged view of a central portion thereof.

As shown in fig. 10(a) and (B), a bottom plate 10B provided on the orbiting scroll 9 is fixed near the discharge port by a fixing screw 33. In order to prevent the lap 3 of the fixed scroll 1 from coming into contact with the fixing screw 33, the lap 3 is not passed.

According to the present embodiment, since the base plate 2B provided in the fixed scroll 1 or the base plate 10B provided in the orbiting scroll 9 is fixed by the fixing screw, the base plate 10B or 2B can be prevented from being turned, the root of the scroll wrap or the base plate can be prevented from being worn, and the reliability can be improved.

Example 3

As described in embodiment 1, in the scroll air compressor, the scroll lap 11(3) and the bottom plate 10B (2B) are formed with a predetermined radial gap in order to improve assemblability. In example 3, the sliding surface of the sheet seal 6 does not fall off the bottom plate 10B even when the bottom plate 10B (2B) moves in the radial direction.

Fig. 11 is a diagram showing a general positional relationship between the bottom plate 10B (2B) and the sheet-like sealing member 6(14), and is a partially enlarged view of fig. 1. In FIG. 11, when the gap between the base plate and the wrap is G, the gaps on both sides of the base plate 10B are G1 and G2, the tooth thickness of the wrap is t, the radius of rotation of the orbiting scroll is ε, and the width of the base plate 10B is Wp,

G＝g1+g2＝2ε+t－Wp。

fig. 12 shows the positional relationship between the bottom plate 10B (2B) and the sheet-like sealing members 6(14) in example 3. When the crest width of the lap portion 11 on the sheet side is w,

g is set to be more than 0 and less than or equal to w.

Since G is set to be equal to or less than w, even when the bottom plate 10B (2B) moves to the maximum extent to one side in the gap, the sliding surface of the sheet seal 6(14) does not come off from the bottom plate 10B (2B), and abnormal wear of the sheet seal 6(14) does not occur. Further, since 0 < G is set, the bottom plate 10B (2B) can be easily attached and detached, and the replaceability during maintenance is good.

Fig. 13 shows another positional relationship between the bottom plate 10B (2B) and the sheet-like sealing member 6(14) for comparison. In this example, when the bottom plate 10B (2B) is moved to the maximum extent to one side in the gap because w < G is set, the sliding surface of the sheet seal 6(14) is separated from the bottom plate 10B (2B), and abnormal wear of the sheet seal 6(14) occurs.

According to the present embodiment, when the bottom plate moves to the maximum extent to one side in the gap, the sliding surface of the sheet seal does not come off from the bottom plate, and therefore, abnormal wear or the like of the sheet seal does not occur.

Example 4

Fig. 14 shows a scroll type air compressor according to embodiment 4 of the present invention. Example 4 is an example in which the base plate 10B (2B) is provided in a conventional scroll air compressor which does not include the base plate 10B (2B).

In the case where the base plates 10B and 2B are provided in a conventional scroll air compressor having no base plate, the distance between the housing 47 and the fixed scroll 2 is increased by the thickness of the base plates 10B and 2B. Therefore, in the present embodiment, the space adjusting members 47A and 47B are provided between the housing 47 and the fixed scroll 2. It is preferable that the thickness of the interval adjusting members 47A and 47B is set to the thickness of the bottom plates 10B and 2B. The interval adjustment members 47A and 47B may be located on both sides with the rotation shaft therebetween.

According to the present embodiment, the base plate can be mounted well in the conventional scroll air compressor without the base plate.

While the embodiments have been described above by taking a scroll air compressor as an example, the present invention can be applied to all scroll fluid machines such as an air compressor and a vacuum pump.

Description of the reference numerals

1 … fixed scroll

2. 10 … end plate

3. 11 … roll body part

11E … winding end part

5. 13 … groove

6. 14 … sheet seal

7. 15 … lower lip

8. 16 … inner lip

9 … orbiting scroll

10B, 2B … baseboard

Hole of 10C … bottom plate

Inner wire of 11A … scroll

11B … outer line of roll body

17 … driving shaft

18 … swivel bearing

19 … suction inlet

20 … discharge port

31. 32, 33 … fixing screw

47 … casing

47A, 47B … size adjustment components.

Claims

1. A scroll fluid machine, comprising:

a fixed scroll having a spiral wrap portion on a tooth bottom surface of an end plate; and

an orbiting scroll disposed to face the fixed scroll, the orbiting scroll having a spiral wrap on a bottom land of an end plate, the wrap and the wrap of the fixed scroll forming a plurality of compression chambers therebetween,

a groove extending along a tooth crest of the lap is formed in at least one lap of the orbiting scroll and the fixed scroll, a seal member in sliding contact with a tooth bottom surface of the opposite scroll is mounted in the groove, a wear-resistant plate-like member is disposed on the tooth bottom surface opposite to the seal member,

the plate-like member and the spiral wrap portion on which the plate-like member is disposed have a predetermined gap in a winding direction of a spiral,

the inner line side or the outer line side of the spiral wrap of the scroll is in contact with the side surface of the plate-like member and stops rotating, so that the plate-like member and the spiral wrap do not contact each other in the winding direction of the scroll.

2. The scroll fluid machine of claim 1, wherein:

the plate-like member has a substantially constant gap in a radial direction from the spiral wrap of the scroll.

3. The scroll fluid machine of claim 2, wherein:

even when the plate-like member moves in the rotational direction in the radial gap between the plate-like member and the winding body and the radial gap disappears, the gap between the plate-like member and the winding start portion and the winding end portion of the winding body in the winding direction of the scroll can be secured.

4. The scroll fluid machine of claim 1, wherein:

the plate-like member and a spiral wrap portion of the orbiting scroll on which the plate-like member is disposed have a predetermined gap in a winding direction of a spiral,

when the scroll fluid machine is normally operated and rotated in the normal direction, the inner line side of the spiral wrap of the orbiting scroll is brought into contact with the side surface of the plate-like member and stops rotating, so that the plate-like member and the spiral wrap do not come into contact with each other in the winding direction of the scroll.

5. The scroll fluid machine of claim 4, wherein:

when the scroll-type fluid machine is reversed, the outer line side of the spiral wrap of the orbiting scroll comes into contact with the side surface of the plate-like member and stops rotating, so that the plate-like member and the spiral wrap do not come into contact with each other in the winding direction of the spiral.

6. The scroll fluid machine of claim 1, wherein:

the plate-like member and the spiral wrap of the fixed scroll on which the plate-like member is disposed have a predetermined gap in a winding direction of a spiral,

the inner line side or the outer line side of the spiral wrap of the fixed scroll is in contact with the side surface of the plate-like member and stops rotating, so that the plate-like member and the spiral wrap do not contact with each other in the winding direction of the spiral.

7. A scroll fluid machine, comprising:

the plate-like member is fixed to the fixed scroll or the orbiting scroll by a screw.

8. The scroll fluid machine of claim 7, wherein:

the plate-like member is fixed in the suction chamber by screws.

9. The scroll fluid machine of claim 8, wherein:

the plate-like member is fixed to a portion of the winding body where the winding body does not pass by using a screw.

10. The scroll fluid machine of claim 7, wherein:

the plate-like member on the fixed scroll side is fixed to the fixed scroll by a screw near a winding end of an inner line of the lap of the fixed scroll.

11. The scroll fluid machine of claim 7, wherein:

the plate-like member on the orbiting scroll side is fixed to the orbiting scroll by a screw near a winding end of an inner line of the lap of the fixed scroll.

12. The scroll fluid machine of claim 7, wherein:

the plate-like member on the orbiting scroll side is fixed to the orbiting scroll by a screw in a discharge chamber.

13. The scroll fluid machine according to any one of claims 1 to 12, wherein:

a size adjustment member having the same thickness as the plate-like member is disposed on a mating surface between the housing and the fixed scroll together with the plate-like member.