JP2007100516A - Scroll fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll fluid machine capable of adjusting force for pressing a seal member to an end plate of a mating scroll or a wall surface of a groove by adjusting the area except for a side surface of the seal member fitted in this groove in design by arranging the groove in an addendum of a lap part of the scroll. <P>SOLUTION: This scroll fluid machine is composed of the grooves 5, 13 arranged in the addendum of the spiral lap parts 3B, 11B, and the seal members 6, 14 fitted in these grooves 5, 13. Lip parts 7, 8 are arranged in a plurality in the longitudinal direction of these seal members 6, 14 for defining high pressure side and low pressure side differential pressure chambers 20A, 20B, 21A and 21B by cutting off air flowing along the inside of the grooves by projecting from the seal members 6 and 14. Pressure receiving surfaces 7A and 8A for directly receiving pressure in at least one differential pressure chambers 20A, 20B, 21A and 21B on the high pressure side and the low pressure side, are arranged in these lip parts 7 and 8 to extend in the longitudinal direction of the seal members 6, 14. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a scroll type fluid machine used for an air compressor, a vacuum pump and the like.

  2. Description of the Related Art Conventionally, a scroll fluid machine is known in which a rectangular groove is provided along a tooth tip of a scroll lap portion, and a seal member is inserted into the groove (see, for example, Patent Document 1).

  The seal member has a rectangular cross section, and a plurality of bottom surface lip portions that are in contact with the bottom surface of the groove are formed on the bottom surface by making a cut perpendicular to the longitudinal direction of the seal member. Also, a plurality of side lip portions that contact the inner wall surface of the groove are provided by making similar cuts on the inner surface of the seal member.

  When the compressed air enters the groove, the bottom lip portion receives the compressed air and elastically deforms toward the bottom surface of the groove. Further, the side lip portion is elastically deformed toward the inner wall surface of the groove.

  Both the lip portions act so as to prevent the compressed air that has entered the groove from flowing along the groove.

  Then, when the bottom surface of the seal member receives the pressure of the compressed air between the lip portions, the seal member floats and the upper surface is pressed against the end plate of the other scroll. Further, when the inner side surface of the seal member receives pressure, the outer side surface of the seal member is pressed against the outer wall surface of the groove.

  And the compression chamber defined by each lap is reliably sealed.

In such a conventional scroll type fluid machine, the force that presses the upper surface of the seal member against the end plate of the other scroll or the force that presses the outer surface of the seal member against the outer wall surface of the groove in a steady operation state is compressed air. It is determined by the area of the bottom or inner surface of the seal member that receives pressure.
Therefore, in the conventional scroll type fluid machine, the setting of the pressing force of the seal member at the design stage is performed by adjusting the area of the bottom surface or the inner surface of the seal member.

JP-A-8-93669

  However, when the area of the bottom surface or the inner surface of the seal member is changed, it is necessary to provide a groove corresponding to the size and shape of the seal member.

  That is, if the area of the bottom or inner surface of the seal member is increased, the size of the groove needs to be increased, so the scroll must be enlarged, and the area of the bottom or inner surface of the seal member is increased. If it is narrowed, the strength of the sealing member is lowered.

  Therefore, the present invention provides a scroll type fluid machine that can adjust the force for pressing the seal member against the end plate of the other scroll or the wall surface of the groove at the time of design by adjusting other than the area of the bottom surface or the inner surface of the seal member. To do.

  In order to solve the above-mentioned problem, the present invention provides, as described in claim 1, one scroll having a wrap portion formed in a spiral shape on a mirror plate, and a mirror plate provided to face the one scroll. The other scroll having a wrap portion formed in a spiral shape, a groove provided along a tooth tip of at least one of the wrap portions of the scrolls, and the groove fitted into the groove. A scroll type fluid machine having a seal member having a plurality of lip portions that project so as to block air flowing along the inside thereof and define a differential pressure chamber on a high pressure side and a low pressure side. The present invention provides a scroll type fluid machine characterized in that a pressure receiving surface that directly receives pressure in the differential pressure chamber on at least one of a side and a low pressure side is provided so as to extend in the longitudinal direction of the seal member.

  According to a second aspect of the present invention, there is provided the scroll type fluid machine according to the first aspect, wherein the pressure receiving areas of the pressure receiving surfaces of the plurality of lip portions are at least two types. A fluid machine is provided.

  According to a third aspect of the present invention, in the scroll fluid machine according to the first or second aspect, the cross-sectional shape of the groove is a rectangle including an inner wall surface, an outer wall surface, and a bottom surface. The lip portion is a rectangle whose cross-sectional shape is composed of an upper surface that contacts the end plate of the other scroll, a lower surface that faces the bottom surface, an inner surface that faces the inner wall surface, and an outer surface that faces the outer wall surface. Is provided on at least one of the lower side surface and the inner side surface of the seal member, and is formed so as to protrude toward the bottom surface or the inner wall surface of the groove.

  According to claim 1, the scroll fluid machine according to the present invention has a pressure receiving surface that directly receives pressure in the differential pressure chamber on at least one of the high pressure side and the low pressure side on the lip portion. Since it is configured to extend in the direction, the pressure receiving area of the pressure receiving surface of the lip portion can be arbitrarily set at the design stage, and the seal member is attached to the end plate of the other scroll, the side surface of the groove, or the like. The degree of freedom when predetermining the pressing force is expanded.

  According to the second aspect of the present invention, since the pressure receiving areas of the pressure receiving surfaces of the plurality of lip portions are at least two types, the pressure receiving areas of the pressure receiving surfaces differ depending on the position in the longitudinal direction of the seal member. The pressing force can be set finely.

  According to the invention described in claim 3, since the lip portion is provided on at least one of the lower side surface and the inner side surface of the seal member and protrudes toward the bottom surface or the inner wall surface of the groove, Compressed air is received by the pressure receiving surface of the lip portion, and the pressing force of the upper surface of the seal member against the end plate of the other scroll or the outer surface of the seal member against the outer wall surface of the groove can be individually adjusted.

  DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of a scroll type fluid machine according to the present invention will be described with reference to preferred embodiments shown in the drawings.

  As shown in FIG. 1, a scroll fluid machine according to the present invention includes a bottomed cylindrical casing 1 having one end opened, a fixed scroll 3 attached to one end of the casing 1, and the other end of the casing 1. An electric motor 2 mounted on the side, a drive shaft 9 rotatably provided on a rotating shaft 2A of the electric motor 2, and a wrap portion 3B of the fixed scroll 3 provided rotatably on the front end side of the drive shaft 9. The orbiting scroll 11 having a lap portion 11B that defines a plurality of compression chambers 17 therebetween.

  The fixed scroll 3 is generally composed of a disc-shaped end plate 3A and a spiral wrap portion 3B standing on the surface side of the end plate 3A, and forms a groove 5 along the tooth tip of the wrap 3B. A spiral seal member 6 is inserted into the groove 5.

  Here, the groove 5 is formed at the intermediate portion in the width direction of the wrap portion 3B, and extends from the winding start end to the winding end end along the spiral shape of the wrap portion 3B. As shown in FIG. 7, this is a rectangle composed of a bottom surface 5A, an inner wall surface 5B, and an outer wall surface 5C.

  The seal member 6 includes a lower side surface 6A that faces the bottom surface 5A of the groove 5, an upper side surface 6B that faces the lower side surface 6A in the vertical direction and contacts the surface of the end plate 11A of the orbiting scroll 11, and an inner wall surface 5B of the groove 5. The seal member 6 that faces the outer wall surface 5C and has a spiral shape includes an inner side surface 6C and an outer side surface 6D that are positioned on the radially inner side and the outer side, and has a rectangular cross-sectional shape.

  The seal member 6 is inserted into the groove 5 with the inner side surface 6C and the outer side surface 6D having a slight gap in the groove 5, and turns as a counterpart from the bottom surface 5A of the groove 5 as will be described later. It can float toward the surface of the end plate 11A of the scroll 11.

  A cylindrical suction port 15 that sucks air into the outermost compression chamber 17 is attached to the outer peripheral side of the fixed scroll 3, and the center of the fixed scroll 3 is compressed in the central compression chamber 17. A cylindrical discharge port 16 for discharging the compressed air to the outside is attached.

  The drive shaft 9 is rotationally driven by the electric motor 2 in a state where the base end side is screwed to the rotating shaft 2 </ b> A of the electric motor 2 and is supported by the main bearing 10 provided at the central portion of the casing 1. . An eccentric bush 4 having a substantially cylindrical shape is attached to the distal end side of the drive shaft 9.

  The orbiting scroll 11 is generally composed of a disc-shaped end plate 11A and a spiral wrap portion 11B standing on the surface side of the end plate 11A, and forms a groove 13 along the tooth tip of the wrap portion 11B. In the groove 13, a spiral seal member 14 is fitted in the same manner as the fixed scroll 3.

  Further, a cylindrical boss portion 11 </ b> C is protruded from the rear side of the end plate 11 </ b> A of the orbiting scroll 11 so as to be located at the central portion thereof. A slewing bearing 12 is attached to the outer peripheral side of the boss portion 11 </ b> C, and the slewing bearing 12 is inserted into the slewing bearing hole 4 </ b> A of the eccentric bush 4.

  Further, a ball coupling 30 serving as an anti-rotation mechanism is attached between the rear surface side of the end plate 11 </ b> A of the orbiting scroll 11 and the casing 1 so as to be positioned at the outer peripheral portion.

  In addition, since the shape and structure of the groove | channel 13 and the sealing member 14 are substantially the same as the said groove | channel 5 and the sealing member 6, the description is abbreviate | omitted.

  As shown in FIG. 1, the fixed scroll 3 and the orbiting scroll 11 are configured such that the wrap portion 11 </ b> B of the orbiting scroll 11 is wrapped with the fixed scroll 3 while the axis OO is decentered by the dimension δ with respect to the axis P-P. It arrange | positions so that it may overlap with respect to the part 3B. Thereby, when this turning scroll 11 is turned with respect to the fixed scroll 3, a plurality of compression chambers 17, 17,... Whose volume changes between the respective lap portions 3B, 11B according to the turning is defined. It has become so.

  Next, details of the seal member 6 will be described. Since the seal member 14 has the same configuration as the seal member 6, the description thereof is omitted.

  First, the bottom lip portion 7 provided on the lower surface 6A of the seal member 6 will be described.

  As shown in FIGS. 3 and 4, the lower surface 6 </ b> A of the seal member 6 has air flowing between the bottom surface 5 </ b> A of the groove 5 and the lower surface 6 </ b> A of the seal member 6 along the groove 5 during operation. A plurality of bottom lip portions 7 are provided as lip portions that protrude so as to block the lip.

  As shown in FIG. 3, the bottom lip portion 7 obliquely cuts the cut lines 6 </ b> K at regular intervals along the longitudinal direction A of the seal member 6 from the lower side surface 6 </ b> A to the upper side surface 6 </ b> B side. It is provided as a thin lip portion.

  As shown in FIG. 4, the cut line 6K is cut from a straight cut start line 6E to a straight cut end line 6F indicated by a one-dot chain line in the drawing.

  Further, the cut start line 6E and the cut end line 6F are inclined with respect to the inner surface 6C or the outer surface 6D of the seal member 6 in a state where the seal member 6 is linearly extended, and are substantially parallel to each other. It is.

  By inserting this cut line 6K, the bottom lip portion 7 is moved from the high pressure side (left in FIG. 3) to the low pressure side (right in FIG. 3) by the pressure of compressed air that has entered the groove 5 during operation. ) And projecting so as to block the air flowing along the groove 5, thereby defining the high pressure side differential pressure chamber 20 </ b> A and the low pressure side differential pressure chamber 20 </ b> B.

  Here, “blocking air” means blocking the air flow to such an extent that the bottom lip 7 generates a differential pressure between the high pressure side differential pressure chamber 20A and the low pressure side differential pressure chamber 20B. It may leak a little.

  As shown in FIGS. 3 and 4, the bottom lip portion 7 has side surfaces formed so as to protrude toward the bottom surface 5 </ b> A of the groove 5 and extend in the longitudinal direction A of the seal member 6. The pressure receiving surface 7A directly receives the pressure of the compressed air inside.

  Since the pressure receiving surface 7A is formed with the angle α inclined with respect to the inner surface 6C and the outer surface 6D of the seal member 6 in a state where the seal member 6 is linearly extended, the compressed air that has entered the groove 5 is formed. The pressure in the differential pressure chambers 20A and 20B acts as a force Ft on the point P of the pressure receiving surface 7A. The force Ft is a force acting in the outer peripheral direction of the fixed scroll 3 as shown by an arrow in the figure, that is, a force Fa that brings the outer surface 6D of the seal member 6 into contact with the outer wall surface 5C of the groove 5, and a groove 5 can be decomposed into a force Fb acting in the vortex direction, and the outer surface 6B of the seal member 6 can be brought into contact with the outer wall surface 5C of the groove 5 by this force Fa.

  Therefore, when the angle α is set to be small at the time of designing, the force Fa for pressing the outer surface 6D of the seal member 6 against the outer wall surface 5C of the groove 5 is increased. On the other hand, when the angle α is set to be large, the pressing force Fa is decreased. Become.

  Here, since the length of the groove 5 in the vortex direction substantially matches the entire length of the seal member 6, the seal member 6 moves in the vortex direction in the groove 5 by the force Fb acting in the vortex direction of the groove 5. There is almost nothing.

  Next, the side lip portion 8 provided on the inner side surface 6C of the seal member 6 will be described.

  As shown in FIGS. 5 and 6, the inner surface 6C of the seal member 6 flows along the groove 5 between the inner wall surface 5B of the groove 5 and the inner surface 6C of the seal member 6 during operation. A plurality of side lip portions 8 are provided as lip portions protruding so as to block air.

  As shown in FIG. 5, the side lip portion 8 is formed so that the cut lines 6 </ b> L are spaced at regular intervals along the longitudinal direction B of the seal member 6 from the inner side surface 6 </ b> C to the outer side surface 6 </ b> D side. It is provided as a thin lip portion.

  As shown in FIG. 6, the cut line 6L is cut from a straight cut start line 6G to a straight cut end line 6H indicated by a one-dot chain line in the drawing.

  Further, the cutting start line 6G and the cutting end line 6H are inclined with respect to the lower side surface 6A or the upper side surface 6B of the sealing member 6 in a state where the sealing member 6 is linearly extended, and are substantially parallel to each other. It is.

  By inserting this cut line 6L, the side lip portion 8 is moved from the high pressure side (upper side of FIG. 5) to the lower pressure side (lower side of FIG. 5) due to the pressure of compressed air that has entered the groove 5 during operation. ), And protrudes so as to block the air flowing along the groove 5, thereby defining the high-pressure side differential pressure chamber 21A and the low-pressure side differential pressure chamber 21B.

  Here, “blocking the air” means blocking the air flow to such an extent that the differential pressure between the high-pressure side differential pressure chamber 21A and the low-pressure side differential pressure chamber 21B is generated by the side lip portion 8. It may leak a little.

  As shown in FIGS. 5 and 6, in the side lip portion 8, the side surface formed so as to protrude toward the inner side surface 6 </ b> C of the groove 5 and extend in the longitudinal direction B of the seal member 6 includes the differential pressure chamber 21 </ b> A, It becomes the pressure receiving surface 8A that directly receives the pressure of the compressed air in 21B.

  Since the pressure receiving surface 8A is formed with the angle β inclined with respect to the inner surface 6C and the outer surface 6D of the seal member 6 in a state where the seal member 6 is linearly extended, the compressed air that has entered the groove 5 is formed. The pressure in the differential pressure chambers 21A and 21B acts as a force Fs on the point Q of the pressure receiving surface 8A. This force Fs is a force acting in the axial direction of the fixed scroll 3 as indicated by an arrow in the figure, that is, a force Fc that brings the upper side surface 6B of the seal member 6 into contact with the surface of the end plate 11A of the other orbiting scroll 11. Then, the force Fd acting in the vortex direction of the groove 5 can be decomposed, and the upper surface 6B of the seal member 6 can be brought into contact with the surface of the end plate 11A of the other orbiting scroll 11 by this force Fc.

  Therefore, when the angle β is set to be small at the time of design, the force Fc that presses the upper surface 6B of the seal member 6 against the surface of the end plate 11A of the other orbiting scroll 11 is increased, whereas when the angle β is set to be large, the seal The force Fc that presses the upper surface 6B of the member 6 against the surface of the end plate 11A is reduced.

  Here, since the length of the groove 5 in the vortex direction substantially matches the entire length of the seal member 6, the seal member 6 moves in the vortex direction in the groove 5 by the force Fd acting in the vortex direction of the groove 5. There is almost nothing.

  Further, the sealing members 6 and 14 are made of an elastic resin material excellent in wear resistance and slidability, for example, a fluorine resin such as polytetrafluoroethylene (PTFE), polyethersulfone (PES), polyphenylene sulfide (PPS). ), Polyether ether ketone (PEEK), liquid crystal polymer (LCP) or polysulfone (PSF).

  The scroll type air compressor according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when the drive shaft 9 is rotationally driven from the outside of the casing 1 by the electric motor 2, this rotation is transmitted from the eccentric bush 4 attached to the tip of the drive shaft 9 to the orbiting scroll 11 via the orbiting bearing 12, The orbiting scroll 11 performs an orbiting motion having an orbiting radius of dimension δ around the axis OO of the drive shaft 9.

  The compression chambers 17, 17,... Defined between the wrap portions 3B, 11B by this turning motion are continuously reduced toward the center side, and the air sucked from the suction port 15 is sequentially compressed. The compressed air is discharged from the discharge port 16 toward an external air tank (not shown).

  Here, when the compression operation is started, a part of the compressed air enters into the grooves 5 and 13 of the wrap portions 3B and 11B from the compression chamber 17 on the high-pressure side, for example, the seal member 6 on the fixed scroll 3 side. Receives the pressure of compressed air by the lower surface 6A of the seal member 6 and the pressure receiving surface 8A of the side lip portion 8 so that it floats up from the inside of the groove 5 and turns the upper surface 6B of the seal member 6 as a counterpart. The outer surface 6D of the seal member 6 can be brought into contact with the surface of the 11 end plates 11A and the pressure of compressed air is received by the inner surface 6C of the seal member 6 and the pressure receiving surface 7A of the bottom lip 7. The outer wall surface 5C of the groove 5 can be contacted.

  Therefore, it is possible to prevent the compressed air from leaking from the distal end portion of the wrap portion 3 toward the radial direction of the fixed scroll 3.

  Further, each bottom lip portion 7 and side lip portion 8 formed on the seal member 6 are elastic at their tip portions toward the bottom surface 5 </ b> A and the inner wall surface 5 </ b> B of the groove 5 due to the pressure of compressed air that has entered the groove 5. By deforming, the air flowing through the gap formed by communicating in the vortex direction between the bottom surface 5A and the inner wall surface 5B of the groove 5 and the seal member 6 is blocked, and the high pressure side is transmitted through this gap. It is possible to prevent the compressed air from leaking from the compression chamber 17 toward the compression chamber 17 on the low pressure side.

  In the embodiment, the case where the fixed scroll 3 and the orbiting scroll 11 are used has been described as an example. However, the present invention is not limited to this, and for example, two scrolls facing each other rotate. A configuration using a double-tooth type having two compression chambers by forming a wrap portion on both surfaces of the entire system rotating type (both rotating type) and the end plate of the orbiting scroll and providing a fixed scroll on each wrap portion side. It is good.

  Moreover, in the said embodiment, the grooves 5 and 13 are formed in the lap | wrap part 3B of the fixed scroll 3, and the lap | wrap part 11B of the turning scroll 11, respectively, and the sealing members 6 and 14 are inserted in these grooves 5 and 13. However, the present invention is not limited to this, and a groove is formed in one of the wrap portion 3B of the fixed scroll 3 and the wrap portion 11 of the orbiting scroll 11, and a seal member is inserted into the groove. You may comprise.

  In the above embodiment, the bottom lip portion 7 is integrally formed on the lower side surface 6A of the seal member 6 and the side lip portion 8 is integrally formed on the inner side surface 6C of the seal member 6. Not only this but you may comprise so that a lip | rip part may be formed in any one side among the lower side 6A, the inner side 6C, and the outer side 6D of the sealing member 6.

  Moreover, in the said embodiment, although the cross-sectional shape of the groove | channel 5 and the sealing member 6 was made into the rectangle, this invention is not restricted to this, You may comprise so that the said cross-sectional shape may be a triangle, trapezoid, or a semicircle. . For example, when the cross-sectional shapes of the groove 5 and the seal member 6 are triangular, the two side surfaces of the seal member are inserted so as to face the high-pressure side wall surface and the low-pressure side wall surface of the groove, The air flowing between the groove and the seal member can be shut off during operation only by providing the lip portion only on the side surface of the seal member facing the wall surface. Further, by receiving pressure at the pressure receiving surface of the lip portion, the seal member can be pressed against the surface of the end plate of the other scroll and the wall surface on the low pressure side of the groove.

  In the embodiment, the pressure receiving surface 7A of each bottom lip 7 is formed so that the pressure receiving area for receiving air pressure is substantially the same, and the pressure receiving area of the pressure receiving surface 8A of each side lip 8 is also the same. Although formed to be substantially the same, the present invention is not limited to this, and as shown in FIG. 8, the inclination angles γ1, γ2, γ3, γ4,... may be set.

  For example, the inclination angle γ of each pressure receiving surface 63 with respect to the upper side surface 61 or the lower side surface 62 of the sealing member 60 is set to gradually decrease from the high pressure side to the low pressure side from the high pressure side of the sealing member 60 (γ1). By satisfying <γ2 <γ3 <γ4), the pressure receiving area of the lip portion becomes smaller on the high pressure side in the groove 5 because the inclination angle γ1 of the pressure receiving surface 63 is larger than the inclination angle γ4 of the pressure receiving surface 63 on the low pressure side. The mechanical loss can be reduced when the upper surface 61 of the seal member 60 is prevented from coming into contact with the surface of the end plate of the other scroll at a high surface pressure and the scroll is swung. On the other hand, since the inclination angle γ4 of the pressure receiving surface 63 on the low pressure side is smaller than the inclination angle γ1 of the pressure receiving surface 63 on the high pressure side, the pressure receiving area of the lip portion becomes large, and the upper side surface 61 of the seal member 60 is placed on the surface of the end plate. The pressing force can be increased.

  Further, in the above-described embodiment, the pressure receiving surfaces for directly receiving the air pressures of the high pressure side differential pressure chambers 20A and 21A and the low pressure side differential pressure chambers 20B and 21B are formed on the bottom lip portion 7 and the side lip portion 8, respectively. However, the present invention is not limited to this, and may be configured to form a pressure receiving surface that receives the air pressure of either the high pressure side differential pressure chamber or the low pressure side differential pressure chamber. Good. For example, as shown in FIG. 9, a low pressure is applied to the side lip portion 30 that is formed by projecting as shown in FIG. 9B so as to block air flowing along the groove on the inner wall surface of the groove. It is also possible to form only the pressure receiving surface 34 that directly receives the uniform pressure in the differential pressure chamber 31 on the side, so that the seal member 35 receives the air pressure received by the lower surface 33 of the seal member 35 and the pressure receiving surface. The air pressure received by the air pressure 34 rises from the bottom surface 5A of the groove 5, and the upper side surface 37 of the seal member 35 can be brought into contact with the surface of the end plate of the other scroll.

  In the above embodiment, the bottom lip portion 7 is elastically deformed from the high pressure side to the low pressure side of the compressed air and hermetically seals between the bottom surface 5A of the groove 5 and the seal member 6, while the side lip portion 8 is configured to be elastically deformed from the high pressure side to the low pressure side of the compressed air and hermetically seal between the inner wall surface 5B of the groove 5 and the seal member 6. However, the present invention is not limited to this, and the groove 10 (b) and FIG. 10 (b) and FIG. 10 (b) and FIG. 10 (b) and FIG. 10 (b) and FIG. As shown in 11 (b), it may be formed by protruding by molding. For example, as shown in FIGS. 10 and 11, the pressure receiving surfaces 44 a and 54 a that directly receive the air pressure in the high pressure side differential pressure chambers 42 and 52 and the air pressure in the low pressure side differential pressure chambers 41 and 51 are directly received. The pressure receiving surfaces 44b and 54b may be formed on the lip portions 40 and 50 so as to extend in the longitudinal direction C of the seal members 45 and 55.

  Further, in the above embodiment, the case where the scroll type fluid machine is used as the scroll type air compressor has been described as an example. However, the present invention is not limited to this, and is applied to, for example, a vacuum pump, a refrigerant compressor, and the like. Is also good.

  In addition, the “pressure receiving surface” defined in the present invention is located at an intermediate portion in the short direction perpendicular to the longitudinal direction of the seal member so as to extend in the longitudinal direction of the seal member. It is a surface that directly receives a uniform pressure in at least one of the differential pressure chambers.

  Therefore, for example, in the embodiment shown in FIG. 9, side surfaces 36a, 36b, and 36c extending in the short direction D of the seal member 35 are formed on the side lip portion 30, but these are the longitudinal directions of the seal member. Since it is not a surface extending in the direction, it does not correspond to the “pressure receiving surface” defined in the present invention.

  The side lip portion 30 is formed with end surfaces 36d and 36e extending in the longitudinal direction C of the seal member 35. These are surfaces provided at the intermediate portion in the short direction D of the seal member 35. In addition, it is a surface that receives non-uniform pressure generated between the end plate 36d of the other scroll and the end surface 36d, or non-uniform pressure generated between the bottom surface 36e of the groove and the end surface 36e. It does not correspond to the “pressure receiving surface” that directly receives the uniform pressure in the differential pressure chamber 31.

  In the above description, the definition of the “pressure receiving surface” has been described by taking the case of the side lip portion as an example, but the present invention is not limited to this, and the same applies to the case of the bottom lip portion.

1 is a schematic partial longitudinal sectional view showing an embodiment of a scroll type fluid machine according to the present invention. FIG. 2 is a schematic partial cross-sectional view as seen from the direction of arrows aa in FIG. 1. The schematic longitudinal cross-sectional view which shows the state which the bottom lip | rip part 7 of the sealing member 6 of FIG. 1 opened. The schematic plan view which shows the closed state of the bottom face lip | rip part 7 of FIG. The schematic longitudinal cross-sectional view which shows the state which the side lip | rip part 8 of the sealing member 6 of FIG. 1 opened. The schematic plan view which shows the closed state of the side lip | rip part 8 of FIG. FIG. 6 is a schematic longitudinal sectional view as seen from the direction of arrows bb in FIG. 5. The schematic plan view which shows other embodiment of this invention. The schematic plan view which shows other embodiment of this invention. The schematic plan view which shows other embodiment of this invention. The schematic plan view which shows other embodiment of this invention.

Explanation of symbols

3 fixed scroll 3A end plate 3B wrap 5 groove 6 seal member 7 bottom lip 7A pressure receiving surface 8 side lip 8A pressure receiving surface 11 orbiting scroll 11A end plate 11B wrap 13 groove 14 seal member 17 compression chamber 20A differential pressure chamber 20B differential pressure chamber 21A Differential pressure chamber 21B Differential pressure chamber

Claims (3)

One scroll with a wrap portion formed in a spiral shape on the end plate,
The other scroll which is provided facing the one scroll and has a wrap portion formed in a spiral shape on the end plate;
A groove provided along a tooth tip of at least one of the wrap portions of the scrolls;
A seal member fitted in the groove;
A plurality of lip portions are provided in the longitudinal direction of the seal member, and a lip portion that defines a differential pressure chamber on the high-pressure side and the low-pressure side by blocking the air that protrudes from the seal member and flows along the groove. In a scroll fluid machine,
A scroll type fluid machine, wherein the lip portion is provided with a pressure receiving surface that extends in the longitudinal direction of the seal member and directly receives the pressure in at least one of the differential pressure chambers on the high pressure side and the low pressure side.   2. The scroll fluid machine according to claim 1, wherein the pressure receiving areas of the pressure receiving surfaces of the plurality of lip portions are at least two types. 3. The scroll fluid machine according to claim 1, wherein a cross-sectional shape of the groove is a rectangle including an inner wall surface, an outer wall surface, and a bottom surface, and the cross-sectional shape of the seal member is in contact with the end plate of the other scroll. A rectangular shape comprising a side surface, a lower surface facing the bottom surface, an inner surface facing the inner wall surface, and an outer surface facing the outer wall surface, and the lip portion is at least of the lower surface and the inner surface of the seal member A scroll type fluid machine provided on one side and projecting toward a bottom surface or an inner wall surface of the groove.

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