WO2018147338A1

WO2018147338A1 - Tip seal for scroll compressor

Info

Publication number: WO2018147338A1
Application number: PCT/JP2018/004250
Authority: WO
Inventors: 石井　卓哉; 大地伊藤; 勝史竹尾; 福澤　覚
Original assignee: Ntn株式会社
Priority date: 2017-02-07
Filing date: 2018-02-07
Publication date: 2018-08-16

Abstract

Provided is a tip seal for a scroll compressor capable of reducing a frictional force between scroll members and the tip seal and contributing to energy saving of the scroll compressor while maintaining sealing performance. A spiral tip seal 1 for sealing a compression chamber formed between a fixed scroll and a movable scroll in a scroll compressor provided with the fixed scroll and the movable scroll serving as scroll members comprises a sliding surface 5 for the scroll members and a plurality of concave parts 4 partially notched in the sliding surface 5. The plurality of concave parts 4 are arranged on at least one of a spiral inner peripheral surface 1b and a spiral outer peripheral surface 1a. Each of the concave parts 4 opens to the inner peripheral surface 1b or the outer peripheral surface 1a and does not penetrate through the inner peripheral surface 1b and the outer peripheral surface 1a.

Description

Scroll compressor tip seal

The present invention relates to a spiral chip seal used in a scroll compressor (compressor).

In a scroll type compressor, a fixed scroll and a movable scroll having a spiral wall standing on the substrate surface and a movable scroll are meshed with each other at the spiral wall, and a compression chamber is formed between them. The compression chamber moves to the spiral center side by the action of a movable scroll that revolves around the axis of the fixed scroll, thereby compressing gas or the like. In order to ensure the tightness of the compression chamber when compressing gas or the like, a seal groove is formed along the spiral extension direction on the end surface of the scroll wall of the fixed scroll and the movable scroll which are the scroll members. Contains a chip seal, which is a seal member that contacts an opposing scroll substrate (end plate).

Such a chip seal is manufactured in a spiral shape in which a long member having a rectangular cross section is wound into a spiral by, for example, injection molding a predetermined synthetic resin (see Patent Document 1). As shown in FIG. 14, this type of tip seal 71 is accommodated in a groove 72a of one wrap (spiral wall) 72 with a gap, and a gas is passed between the end plate (scroll substrate) 73 facing the groove 72a. Due to the pressure of 74, it floats from the groove bottom 72b toward the end plate 73. The floated chip seal 71 is in sliding contact with the end plate 73 at a seal surface 71a which is one surface constituting a rectangular cross section, and seals the compression chamber between the spiral walls.

JP 2002-322988 A

In order to save energy in the scroll compressor, it is important to reduce the torque during scrolling (during operation) by reducing the friction between the scroll member and the tip seal. However, when the cross section of the chip seal is rectangular, the sliding area with the scroll substrate is large, and the frictional force on the sliding surface is large.

The present invention has been made to cope with such problems, and is capable of reducing the frictional force between the scroll member and the tip seal while maintaining the sealing performance, and can contribute to energy saving of the scroll compressor. An object of the present invention is to provide a tip seal.

A tip seal for a scroll compressor according to the present invention is a scroll compressor provided with a fixed scroll and a movable scroll as scroll members, for sealing a compression chamber formed between the fixed scroll and the movable scroll. A tip seal having a spiral shape, wherein the tip seal has a plurality of recesses in which the sliding surface is partially cut out on a sliding surface with the scroll member, and the plurality of recesses are the inner periphery of the spiral. It arrange | positions at least one of a surface and an outer peripheral surface, and each recessed part is characterized by opening to an inner peripheral surface or an outer peripheral surface, and not penetrating an inner peripheral surface and an outer peripheral surface.

The ratio of the total area of the recesses on the sliding surface (the total area of the recesses / (total area of the recesses + actual sliding area) × 100) is 5 to 45%.

The planar shape of the recess is a substantially rectangular shape along an arc shape or a spiral shape.

The depth of the recess is 45% or less of the thickness of the chip seal.

A plurality of the recesses are provided on the sliding surface so as to be spaced apart from each other in the length direction from the winding start end portion to the winding end end portion of the spiral of the chip seal. It is 1 to 20% of the developed length of the seal, and a part of the sliding surface is provided between the adjacent concave portions.

Further, the area of the planar shape of the recess is substantially the same between the recesses. Further, a plurality of the recesses are provided at equal intervals on the sliding surface.

The planar shape of the concave portion is an arc shape, and the arc radius of the concave portion is continuously or gradually increased from the winding start end portion to the winding end end portion of the tip seal spiral. Features.

A tip seal for a scroll compressor according to the present invention is a spiral tip seal for sealing a compression chamber formed between a fixed scroll and a movable scroll which are scroll members in a scroll compressor. Has a groove at the center in the width direction of the chip seal at least on the sliding surface with the scroll member, and the groove is formed over substantially the entire length of the chip seal.

The groove width of the groove is 1/20 to 2/5 of the width dimension of the chip seal.

The groove width increases continuously or stepwise from the winding start end to the winding end of the tip seal spiral.

The groove depth of the groove is 35% or less of the thickness of the chip seal.

The groove is characterized in that an opening connected to the groove is provided on either the inner peripheral surface or the outer peripheral surface of the spiral.

The opening has a concave shape in which the sliding surface is cut out, and a plurality of the openings are provided apart from each other in the length direction from the winding start end to the winding end of the tip seal spiral. And

The above chip seal is made of synthetic resin.

The scroll type compressor chip seal of the present invention is a spiral chip seal for sealing a compression chamber formed between a fixed scroll and a movable scroll as a scroll member, and on a sliding surface with the scroll member, Since the sliding surface has a plurality of recesses partially cut away, the sliding area is reduced and the surface pressure is increased, whereby the frictional force on the sliding surface can be reduced. As a result, the torque at the time of scrolling of the scroll member in the scroll compressor can be reduced, which can contribute to energy saving of the compressor. Further, the plurality of concave portions of the sliding surface are arranged on at least one of the inner peripheral surface and the outer peripheral surface of the spiral, and each concave portion opens on the inner peripheral surface or the outer peripheral surface and penetrates the inner peripheral surface and the outer peripheral surface. Therefore, lubricating oil such as refrigerating machine oil is supplied to the sliding surface while maintaining the sealing performance, and the frictional force on the sliding surface can be further reduced.

Since the ratio of the total area of the recesses on the sliding surface (total area of the recesses / (total area of the recesses + actual sliding area) × 100) is 5 to 45%, the frictional force on the sliding surface is reduced and the machine A decrease in strength is suppressed.

Since the planar shape of the recess is a substantially rectangular shape along an arc shape or a spiral shape, the design and arrangement of the recess is facilitated. In particular, when a plurality of the concave portions are arranged, it is easy to design such that the concave portions have substantially the same area between the concave portions.

Since the depth of the recess is 45% or less of the thickness of the chip seal, it is possible to ensure sufficient sealing performance while providing the recess with the sliding surface partially cut away.

A plurality of recesses are provided on the sliding surface, spaced apart from each other in the length direction from the winding start end to the winding end of the tip seal spiral, and the opening length of each recess is the development of the chip seal. Since it is 1 to 20% of the length and a part of the sliding surface is between adjacent recesses, the sliding area is reduced, and the frictional force on the sliding surface can be further reduced.

Moreover, since the area of the planar shape of the recess is substantially the same, the difference in frictional force between the seal portions is reduced, and stable scrolling of the scroll member becomes possible. In addition, since a plurality of recesses are provided at equal intervals on the sliding surface, a stable scroll member can be scrolled as described above.

The planar shape of the concave portion is an arc shape, and the arc radius of the concave portion installed increases continuously or stepwise from the winding start end portion to the winding end end portion of the tip seal spiral. The area of the planar shape of the recesses can be made substantially the same between the recesses while making the lengths substantially the same.

A tip seal for a scroll compressor according to the present invention is a spiral tip seal for sealing a compression chamber formed between a fixed scroll and a movable scroll as a scroll member, and at least a sliding surface with the scroll member In the chip seal, there is a groove at the center in the width direction, and the groove is formed over the entire length of the chip seal, so that the sliding area is reduced and the surface pressure is increased. The frictional force can be reduced. As a result, the torque at the time of scrolling of the scroll member in the scroll compressor can be reduced, which can contribute to energy saving of the compressor. Moreover, since the said groove | channel functions also as a lubrication groove | channel, it becomes possible to supply lubricating oil, such as refrigerating machine oil, to a sliding surface.

Since the groove width of the groove is 1/20 to 2/5 of the width dimension of the chip seal, the mechanical strength of the seal can be secured while maintaining the sealing performance. Furthermore, since the groove width increases continuously or stepwise from the winding start end portion to the winding end end portion of the tip seal spiral, while maintaining high sealing performance on the inner peripheral side of the spiral, On the outer peripheral side of the spiral, the sliding area becomes smaller, and the frictional force on the sliding surface can be further reduced.

Since the groove depth of the groove is 35% or less of the thickness of the chip seal, the mechanical strength of the seal is prevented from being lowered and sufficient sealing performance can be ensured.

Since the groove is provided with an opening connected to the groove on one of the inner peripheral surface and the outer peripheral surface of the spiral, lubricating oil is introduced into the groove from the opening while maintaining the sealing performance, and the sliding is performed. The frictional force on the moving surface can be made smaller. In addition, the opening has a concave shape with a sliding surface cut out, and a plurality of openings are provided apart in the length direction from the winding start end to the winding end of the tip seal spiral. It is possible to improve the supply performance of the lubricating oil.

Since the chip seal is made of synthetic resin, it has excellent low-friction characteristics and non-aggressiveness to the contact surface of the mating member, contributing to a longer life of the scroll compressor.

It is a top view which shows an example of the chip seal of 1st Embodiment. FIG. 2 is an enlarged view around a recess in FIG. 1. It is sectional drawing of the state which integrated the chip seal in the compressor. It is a top view which shows the other example of the chip seal of 1st Embodiment. FIG. 5 is an enlarged view around a recess in FIG. 4. It is a partial cross section figure of the compression mechanism part of a scroll type compressor. It is a top view which shows an example of the chip seal of 2nd Embodiment. It is sectional drawing of the state which integrated the chip seal in the compressor. It is a figure which shows the cross-sectional shape of a groove | channel. It is a top view which shows the other example of the chip seal of 2nd Embodiment. It is a top view which shows the other example of the chip seal of 2nd Embodiment. It is sectional drawing of the state which integrated the chip seal in the compressor. It is a partial cross section figure of the compression mechanism part of a scroll type compressor. It is sectional drawing of the state which integrated the conventional chip seal in the compressor.

(First embodiment)
An example of the structure of the compression mechanism of the scroll compressor to which the chip seal of the first embodiment is applied will be described with reference to FIG. FIG. 6 is a partial cross-sectional view of the compression mechanism of the scroll compressor. As shown in FIG. 6, the scroll compressor includes a fixed scroll 24 having a substrate 24a and a spiral wall 24b upstanding on the surface thereof, and a movable scroll 25 having a substrate 25a and a spiral wall 25b upstanding on the surface thereof. Yes. The fixed scroll 24 and the movable scroll 25 are engaged with each other at the spiral wall boundary 26 in an eccentric state, and a compression chamber 22 is formed between them. When the movable scroll 25 revolves around the axis of the fixed scroll 24, the compression chamber 22 moves to the center side of the spiral shape, and compression of gas or the like is performed. Seal grooves 23 are formed on the spiral wall end surfaces of the fixed scroll 24 and the movable scroll 25 along the spiral extension direction. The chip seal 21 of the first embodiment is accommodated in the seal groove 23 and is in sliding contact with the opposing scroll substrate to ensure the sealing property of the compression chamber 22.

An example of the scroll compressor tip seal of the first embodiment will be described with reference to FIGS. FIG. 1 is a plan view of the chip seal of the first embodiment as viewed from the sliding surface side with a mating scroll member serving as a seal surface, FIG. 2 is a partially enlarged view thereof, and FIG. It is sectional drawing of the state assembled in the compressor. As shown in FIG. 1, the chip seal 1 has a spiral shape in which a long member having a substantially rectangular cross section is wound around a spiral. This spiral shape is a shape in which the radius of curvature gradually increases from the winding start end 2 toward the winding end end 3. The sliding surface 5 is a sliding surface with the opposing scroll substrate, and serves as a sealing surface that seals gas in the compression chamber.

The chip seal 1 has a plurality of recesses 4 in which the sliding surface 5 is partially cut out on the sliding surface 5 with the scroll member. The plurality of recesses 4 are arranged on the inner peripheral surface 1b of the spiral. In addition, the recessed part 4 is good also as a form arrange | positioned in the outer peripheral surface 1a, and good also as a form arrange | positioned in both the internal peripheral surface 1b and the outer peripheral surface 1a. Each recess opens to the inner peripheral surface 1b or the outer peripheral surface 1a and does not penetrate the inner peripheral surface 1b and the outer peripheral surface 1a. That is, in the chip seal 1 in which the plurality of recesses 4 are formed, the recesses on the inner peripheral surface 1b are not penetrating the outer peripheral surface 1a, and the recesses on the outer peripheral surface 1a are not penetrating the inner peripheral surface 1b. The recess 4 is not formed as a recess closed within the sliding surface, but the edge of the sliding surface 5 is cut out to form a shape opened to the inner peripheral surface 1b or the outer peripheral surface 1a. Therefore, it is easy to supply the lubricating oil to the sliding surface. Moreover, the sealing performance can also be ensured by opening the recess 4 only on one of the inner peripheral surface 1b and the outer peripheral surface 1a of the spiral and making the inner peripheral surface 1b and the outer peripheral surface 1a non-penetrating.

In addition, since the ratio of the total area of the recesses on the sliding surface (the total area of the recesses / (the total area of the recesses + the actual sliding area) × 100) is 5 to 45%, the frictional force on the sliding surface is effective. Can be made smaller. When the ratio of the total area of the recesses on the sliding surface is less than 5%, the surface pressure of the sliding surface cannot be increased effectively, and the effect of reducing the frictional force is poor. On the other hand, if it exceeds 45%, the gas pressure from the concave portion becomes high, the gas pressure from the anti-seal surface is offset, and the surface pressure of the sliding surface decreases, resulting in a poor effect of reducing the frictional force. . Note that the ratio of the total area of the recesses on the sliding surface is preferably 7 to 40%, and more preferably 10 to 35%. The actual sliding area is an area obtained by removing the concave portion from the sliding surface.

Further, in the form shown in FIG. 1, a plurality of recesses 4 are formed on the sliding surface 5 apart from each other in the length direction from the winding start end 2 to the winding end end 3 of the spiral of the chip seal 1 (FIG. 44) installed side by side. Between the adjacent recessed parts 4 is a part of sliding surface 5 (seal surface). The number of the recesses is not particularly limited, and is appropriately set in consideration of the size of each recess. For example, 10 to 50, preferably 30 to 50. The recesses 4 are preferably installed at equal intervals on the sliding surface 5. Thereby, the difference of the frictional force between the seal | sticker parts becomes small, and the scroll of the stable scroll member is attained.

The opening length of each recess 4 is preferably 1% to 20% of the developed length of the chip seal. 1% to 10% is more preferable, and 1% to 5% is more preferable. A large number can be arranged by reducing the opening length. For example, comparing the case where a small number of long concave portions along the spiral are arranged with the case where a plurality of short concave portions are arranged, the latter is more preferable than the former when the total area of the concave portions is the same. It is preferable because it is easy to suppress deformation and the like and has excellent sealing properties. Note that the developed length of the tip seal is a length obtained by developing a spiral long member, which is the center position in the width W direction of the tip seal (from the inner peripheral surface and the outer peripheral surface, etc. in the plan view of FIG. 1). This is the total length of the center line 1c connecting the distance positions. In addition, the opening length of the arc-shaped recess is the maximum length of the arc opening on the inner peripheral surface or outer peripheral surface of the recess (the length along the inner peripheral surface 1b between 4b and 4b in FIG. 2).

As shown in FIG. 2, the planar shape of the recess 4 is an arc. Moreover, as shown in FIG. 3, the cross-sectional shape of the recessed part 4 is made into the rectangle. Therefore, the concave portion 4 has a shape in which the planar shape is an arc shape and is formed perpendicularly from the sliding surface 5 to a certain depth. For this reason, the concave portion 4 has the same planar shape at the sliding surface 5 and the planar shape at the deepest portion 4c. The arc radius R (see FIG. 2) and the center position of the arc surface 4a are not particularly limited, but it is preferable to set the recess so that it does not exceed the center position in the width direction of the chip seal. For example, the radius R is preferably R2 mm to R4 mm when the size of the chip seal (substantially outer diameter of the spiral) is 70 mm. By providing a plurality of recesses so as not to exceed the center position, high sealing performance can be maintained.

The depth d (see FIG. 3) of the recess 4 is preferably 45% or less of the thickness of the chip seal. 30% or less is preferable and 15% or less is more preferable. Note that the thickness T of the chip seal is between the sealing surface, which is a sliding surface, and the anti-sealing surface. By setting the depth of the recess 4 to 45% or less of the thickness of the chip seal, the rigidity of the chip seal can be maintained, and the frictional force on the sliding surface can be appropriately reduced even when wear progresses. As a result, it is possible to secure a sufficient sealing performance while providing a concave portion in which the sliding surface is partially cut to reduce the frictional force.

Further, as shown in the enlarged view in FIG. 2, the boundary portion 4b between the inner peripheral surface 1b of the spiral and the circular arc surface 4a is preferably R-shaped (for example, R 0.5 mm or less). By providing such an R shape, when the inner peripheral surface and the seal groove are in sliding contact, the edge of the boundary portion can be eliminated, and it becomes easier to introduce lubricating oil such as refrigerating machine oil into the recess, A stable lubrication state can be maintained and local deformation of the tip seal can be suppressed.

The area of the planar shape of the recess 4 is preferably substantially the same between the recesses. Thereby, the difference of the frictional force between the seal | sticker parts becomes small, and the scroll of the stable scroll member is attained. Here, as shown in FIG. 1, since the tip seal 1 of the first embodiment has a spiral shape, the radius of curvature gradually increases from the winding start end 2 toward the winding end end 3. For this reason, the recessed part 4 cannot be unified by a single circular arc shape, and the area of the planar shape cannot be made the same. Therefore, in order to make the planar shape area of the recesses substantially the same between the recesses while making the opening lengths of the recesses substantially the same, the tip seal is installed from the winding start end to the winding end end. It is preferable to increase the arc radius of the recessed portion continuously or stepwise. In the form shown in FIG. 1, the concave portion is stepwise divided into three stages: (1) winding start end 2 to X, (2) X to Y, (3) Y to winding end 3. The arc radius is increased.

The chip seal 1 is a seal member for sealing a compression chamber formed between a scroll of a fixed scroll that is a scroll member and a spiral wall of a movable scroll in a scroll compressor. As shown in FIG. 3, the tip seal 1 is accommodated in the seal groove of the spiral wall 7 and is in sliding contact with the opposing scroll substrate 6 to seal the compression chamber. The spiral wall 7 and the scroll substrate 6 are opposed to each other with a gap 8 (opposing distance D). The relationship between the depth d of the recess 4 and the facing distance D of the gap 8 is preferably substantially the same or the depth d of the recess 4 is slightly smaller. The chip seal 1 is accommodated in the seal groove of the spiral wall 7 with a gap, and floats from the bottom of the seal groove toward the scroll substrate 6 due to the pressure of the gas 9 between the tip seal 1 and the opposing scroll substrate 6. The chip seal 1 that has floated is in sliding contact with the scroll substrate 6 at the sliding surface 5 and the seal groove wall 7a of the spiral wall 7 at the outer peripheral surface 1a, and the scroll wall 7 and the scroll of the fixed scroll and the movable scroll as scroll members. The compression chamber between the spiral walls of the substrate 6 is sealed.

Since the chip seal 1 has a plurality of the above-described recesses 4 on the sliding surface 5, a part of the compression chamber gas 9 can be introduced into the recesses 4. Arrows 9a and 9b in the figure indicate the pressure applied to each surface from the gas 9. Due to the recess 4 with the sliding surface 5 partially cut away, the sliding area itself becomes smaller than that of the conventional product (FIG. 14) without the recess. The chip seal (44 recesses) of this embodiment shown in FIGS. 1 to 3 and the conventional chip seal shown in FIG. 14 have the same dimensions except for the presence or absence of recesses. In this case, the actual sliding area is 75 in this embodiment, where the conventional product is 100, and the ratio of the total area of the recesses on the sliding surface (total area of the recesses / (total area of the recesses + actual sliding area) × 100) Is 25%. By reducing the actual sliding area, the surface pressure applied to the sliding surface increases and the friction coefficient decreases. As a result, the frictional force on the sliding surface is reduced. Further, as shown as the gas pressure, in this embodiment, the gas pressure received by the anti-seal surface of the tip seal 1 is partially offset by the gas pressure introduced into the recess 4. However, since lubricating oil such as refrigerating machine oil is easily supplied to the sliding surface, the frictional force on the sliding surface can be greatly reduced as compared with the conventional product. The ratio of the total area of the recesses on the sliding surface (the total area of the recesses / (the total area of the recesses + the actual sliding area) × 100) is 5 to 45%, and if it exceeds 45%, the surface pressure applied to the sliding surface Is reduced by the gas introduced into the recess 4.

Another example of the scroll compressor tip seal of the first embodiment will be described with reference to FIGS. FIG. 4 is a plan view of the chip seal of this embodiment as viewed from the sliding surface side with the mating scroll member serving as the seal surface, and FIG. 5 is a partially enlarged view thereof. As shown in FIGS. 4 and 5, the chip seal 11 has a plurality of recesses 14 in which the sliding surface 15 is partially cut out on the sliding surface 15 with the scroll member. The shape of the recess is a substantially rectangular shape along the spiral shape. Both long sides of the rectangle are curved along the spiral shape, and the concave portion is arranged on the inner peripheral surface 11b of the spiral, and one side of the rectangular long side of each concave portion opens on the inner peripheral surface 11b of the spiral. ing.

The number of recesses, the opening length of each recess, the depth of the recess, and the like are the same as those of the arc-shaped recess shown in FIG. With respect to the planar shape, it is preferable to set so that the recess does not exceed the center position in the width direction of the chip seal.

As described above, by designing the concave portion to have a substantially rectangular shape along the arc shape or the spiral shape, the design and arrangement of the concave portion can be facilitated. In particular, when a plurality of concave portions are arranged, the areas are substantially the same. Such design becomes easy. Moreover, although the chip seal having the concave portion on the sliding surface has been described based on the respective drawings, the present embodiment is not limited to this, and the shape of the concave portion is particularly limited to a plurality of concave portions in which the sliding surface is partially cut out. If the plurality of recesses are disposed on at least one of the inner peripheral surface and the outer peripheral surface of the spiral, and the individual recesses open to the inner peripheral surface or the outer peripheral surface and do not penetrate the inner peripheral surface and the outer peripheral surface. , Can be any shape. For example, the depth of the recess may not be a constant depth, but the deepest portion may have an inclined surface that extends to the opening side such as a hemispherical shape or a tapered shape.

(Second Embodiment)
Next, an example of the structure of the compression mechanism of the scroll compressor to which the chip seal of the second embodiment is applied will be described with reference to FIG. FIG. 13 is a partial cross-sectional view of the compression mechanism of the scroll compressor. As shown in FIG. 13, the scroll compressor includes a fixed scroll 64 having a substrate 64a and a spiral wall 64b upstanding on the surface thereof, and a movable scroll 65 having a substrate 65a and a spiral wall 65b upstanding on the surface thereof. Yes. The fixed scroll 64 and the movable scroll 65 are engaged with each other at the spiral wall boundary 66 in an eccentric state, and a compression chamber 62 is formed between them. When the movable scroll 65 revolves around the axis of the fixed scroll 64, the compression chamber 62 moves to the center side of the spiral shape, and compression of gas or the like is performed. Seal grooves 63 are formed on the spiral wall end surfaces of the fixed scroll 64 and the movable scroll 65 along the spiral extension direction. Similar to the chip seal of the first embodiment, the chip seal 61 of the second embodiment is accommodated in the seal groove 63 and is in sliding contact with the opposing scroll substrate to ensure the sealing property of the compression chamber 62. .

An example of the scroll-type compressor chip seal of the second embodiment will be described with reference to FIGS. FIG. 7 is a plan view of the chip seal of the second embodiment viewed from the sliding surface side with the mating scroll member serving as the seal surface, and FIG. 8 is a cross-sectional view of the chip seal incorporated into the compressor. The tip seal 31 is a seal member for sealing a compression chamber formed between a scroll of a fixed scroll and a scroll of a movable scroll in a scroll compressor. As shown in FIG. 7, the tip seal 31 has a spiral shape in which a long member having a substantially rectangular cross section is wound into a spiral. This spiral shape is a shape in which the radius of curvature gradually increases from the winding start end portion 32 toward the winding end end portion 33. The sliding surface 35 is a sliding surface with the opposing scroll substrate and serves as a sealing surface that seals gas in the compression chamber.

7, the tip seal 31 has a groove 40 formed on the sliding surface 35 with the scroll member over substantially the entire length of the tip seal 31. The groove 40 does not open to the inner peripheral surface 31b of the spiral and the outer peripheral surface 31a of the spiral, but is a concave groove closed within the sliding surface. Further, the groove 40 is provided at a substantially central portion of the chip seal 31 in the width W direction. In FIG. 7, the groove 40 is formed symmetrically about a center line 31 c connecting the center positions in the width W direction of the chip seal 31 (positions equidistant from the inner peripheral surface and the outer peripheral surface). By providing the groove 40 on the sliding surface 35 in this way, the sliding area can be reduced and lubricating oil can be held in the groove to ensure lubricity.

The groove on the sliding surface is provided over almost the entire length of the chip seal. In the second embodiment, the state over substantially the entire length includes not only the continuous state from the winding start end portion 32 to the winding end end portion 33 of the chip seal but also a discontinuous state. For example, as shown in FIG. 7, there may be portions where the groove 40 is not formed on the winding start end 32 side and the winding end end 33 side of the sliding surface 35. Further, the groove 40 may be one continuous concave groove as shown in FIG. 7 or two or more concave grooves divided in the length direction of the spiral of the chip seal 31.

In the second embodiment, since the groove is formed over substantially the entire length of the chip seal, the length of the groove in the length direction of the spiral of the chip seal (the total length of two or more divided concave grooves) ) Is 60% or more of the developed length of the tip seal, more preferably 70% or more, and even more preferably 80% or more. In particular, the groove is preferably a single groove having a length of 80% or more with respect to the developed length of the chip seal. Note that the developed length of the tip seal is the length of a spiral-shaped long member developed, and this is the length of the center line 31c in FIG.

The cross-sectional shape of the groove is a rectangular square groove in FIG. 8, but is not particularly limited as long as it is a shape capable of holding lubricating oil. Another cross-sectional shape of the groove 40 applied to the chip seal 31 is shown in FIG. For example, as the groove, an arc-shaped groove shown in FIG. 9A, a V-shaped groove shown in FIG. 9B, a square groove whose both side surfaces are tapered, or the like can be adopted. Among these, since the supply of the lubricating oil to the sliding surface 35 is smooth, it is preferable to use an arcuate groove or a V groove. Note that the cross-sectional shapes of these grooves can also be applied to a chip seal 41 and a chip seal 51 described later.

In FIG. 8, the groove depth d of the groove 40 is preferably 35% or less of the thickness of the chip seal, more preferably 30% or less, and further preferably 15% or less. Note that the thickness T of the chip seal is between the sealing surface, which is a sliding surface, and the anti-sealing surface. By setting the groove depth d to 35% or less of the thickness of the chip seal, the rigidity of the chip seal is maintained, and even if wear progresses, the frictional force on the sliding surface can be appropriately reduced. Sealability is maintained without deformation. Thereby, sufficient sealing performance can be secured while reducing the frictional force. The groove depth d refers to the maximum depth from the sliding surface 35 in the groove 40. For example, the groove depth d in each groove in FIG. 9 is as shown in the figure.

As shown in FIG. 8, the tip seal 31 is accommodated in the seal groove of the spiral wall 37 and is in sliding contact with the opposing scroll substrate 36 to seal the compression chamber. In FIG. 8, the scroll substrate 36 and the spiral wall 37 are scroll members (fixed scroll or movable scroll), and the scroll member provided with the seal groove is the spiral wall 37 and the other scroll member is the scroll substrate 36. Yes. The spiral wall 37 and the scroll substrate 36 are opposed to each other with a gap 38 (opposite distance D), and the relationship between the groove depth d and the opposed distance D of the gap 38 is substantially the same, or the groove depth d. Is slightly smaller.

The groove width GW (see FIG. 8) of the groove 40 is set to 1/20 to 2/5, and preferably 1/20 to 1/3 of the width dimension of the chip seal. The width dimension W of the chip seal (hereinafter also referred to as the seal width) is the length from the inner peripheral surface to the outer peripheral surface. Further, the actual width of the groove width GW of the groove 40 is required to be 0.1 mm or more. It is not necessary to set the maximum value in actual dimensions. If the groove width GW is less than 1/20 of the seal width or less than 0.1 mm, it is difficult to effectively increase the surface pressure of the chip seal, and the effect of reducing the friction coefficient May not be obtained. On the other hand, the seal width and the mechanical strength are ensured by setting the maximum width of the groove width GW to 2/5 of the seal width. The groove width GW is the length in the width direction of the chip seal at the portion opened to the sliding surface 35. For example, the groove width GW in each groove in FIG. 9 is as shown in the figure.

シール The seal width of the tip seal is related to the compressor capacity, but is approximately in the range of 2 mm to 5 mm. For example, when the seal width is 2 mm, the minimum width of the groove is 1/20 of the seal width, and the actual size is 0.1 mm. When the seal width is 1 mm, the minimum groove width is 0.1 mm (1/10 of the seal width) in actual dimensions. In this case, the maximum width of the groove is 0.40 mm which is 2/5 of the seal width.

Here, in FIG. 7, the groove width of the groove 40 is constant over substantially the entire length of the chip seal 31. For example, the groove width may be set differently from the winding start end 32 toward the winding end end 33 without making the groove width constant. In this case, it is preferable to set the groove width to be different in consideration of the pressure distribution of the compressed gas. Since the scroll compressor gradually compresses gas from the outer peripheral side of the spiral toward the inner peripheral side (center side), the pressure of the compressed gas is higher on the inner peripheral side. It is higher than the club side. For example, since the gas sucked from the suction pipe (not shown) is hardly compressed on the outer peripheral side, the pressure difference between the high pressure side and the low pressure side separated by the tip seal is not so large. Therefore, on the outer peripheral side, it is considered that a sealing function sufficient for compression can be exhibited without giving the chip seal so high sealing performance. On the other hand, since the pressure difference between the high pressure side and the low pressure side is large on the inner peripheral side, it is considered that high sealing performance is required for the chip seal.

In consideration of the above pressure distribution, in the configuration in which the grooves are provided so that the groove widths are different, it is preferable to increase the groove width continuously or stepwise from the winding start end to the winding end. For example, in the chip seal 41 of FIG. 10, the groove 50 is divided into two in the length direction of the chip seal. In this case, when the groove width of the groove 50a on the inner peripheral side is GW1, and the groove width of the groove 50b on the outer peripheral side is GW2, GW2 is larger than GW1. By adopting this configuration, while reducing the sliding area by providing a groove over almost the entire length, the sliding area is further reduced by increasing the groove width on the outer peripheral side, and the groove on the inner peripheral side. By making the width relatively small, high sealing performance can be secured.

As another configuration, in one groove, the groove width may be divided into three or more steps, and may be increased stepwise from the winding start end portion toward the winding end end portion. Alternatively, the groove width may be continuously increased.

As described above, in the chip seal of the second embodiment, the sliding area itself is smaller than the conventional product without the groove due to the groove provided on the sliding surface. The tip seal of this embodiment shown in FIGS. 7 and 10 and the tip seal of the conventional product (FIG. 14) have the same dimensions except for the presence or absence of grooves. In this case, when the conventional product is 100, the actual sliding area is 65 to 97 in this embodiment, and the ratio of the total groove area on the sliding surface (groove total area / (groove total area + actual sliding area) × 100) is 3 to 35%. By reducing the actual sliding area, the surface pressure applied to the sliding surface increases and the friction coefficient decreases. As a result, the frictional force on the sliding surface is reduced.

Another example of the scroll compressor tip seal of the second embodiment will be described with reference to FIG. FIG. 11 is a plan view of a chip seal having a groove and an opening on the sliding surface as viewed from the sliding surface, and FIG. 12 is a cross-sectional view at the position of the opening when the chip seal is incorporated in a compressor. It is. As shown in FIG. 11, an opening 60 c connected to the groove 60 is provided on the inner peripheral surface 51 b of the spiral of the chip seal 51. In FIG. 11, the opening 60 c has a concave shape (concave portion) in which the sliding surface 55 is partially cut out. By providing the opening 60c connected to the groove 60 in this manner, the groove 60 is in communication with the space outside the seal even when the sliding surface 55 is slid with another member. Therefore, the lubricating oil is always supplied to the groove 60 through the opening 60c, and the frictional force on the sliding surface 55 can be further reduced.

In the form shown in FIG. 11, a plurality of openings 60c are spaced apart in the length direction from the winding start end portion 52 to the winding end end portion 53 of the spiral of the chip seal 51 (FIG. Pieces) are installed side by side. The number of openings 60c is not particularly limited, but by using a plurality of openings 60c, the lubricating oil can smoothly enter and exit the groove 60.

In the configuration in which a plurality of openings are provided, adjacent openings may be provided at equal intervals on the inner peripheral surface, or may be provided at different intervals. In the latter case, in particular, in consideration of the pressure distribution described above, it is preferable that the distance between the adjacent opening portions be widened continuously or stepwise from the winding end portion toward the winding start end portion. As described above, since the inner peripheral side of the chip seal is required to have high sealing performance, the interval is widened from the winding end to the winding start end, and the number of openings on the inner peripheral side is set to the outer peripheral side. The sealing performance is ensured by making it less. On the other hand, since the gas pressure on the inner peripheral side is larger than that on the outer peripheral side, it is considered that the lubricating oil can be sufficiently supplied to the groove with a high gas pressure even if the number of openings is small.

In the form shown in FIG. 11, the planar shape of the opening 60c is rectangular, but the present invention is not limited to this. For example, it is good also as a wedge shape, and it is good also considering the side where the convex is spreading as the internal peripheral surface side 51b. In other words, in this case, since the opening length of the opening 60 c is narrowed from the inner peripheral surface 51 b toward the groove 60, the supply of lubricating oil to the groove 60 can be improved. In addition, the opening length may be different between the opening on the inner peripheral side and the opening on the outer peripheral side. For example, by making the opening length of the opening portion on the inner peripheral portion side smaller than the opening length of the opening portion on the outer peripheral portion side, the balance between the sealing property and the supply property of the lubricating oil can be improved.

The depth of the opening 60c in the thickness direction of the chip seal 51 (see FIG. 12) is preferably substantially the same as the groove depth d of the groove 60 or slightly larger than the groove depth d. Thereby, the supply property of the lubricating oil to the groove 60 can be improved.

Also in the configuration of the chip seal 51, the sliding area itself is smaller than the conventional product without the groove due to the groove 60 formed in the sliding surface 55. Further, as shown in FIG. 12, by providing the opening 60c, the chip seal 51 partially introduces the gas 59 in the compression chamber into the groove 60 through the opening 60c.

Arrows

59a and 59b in the figure indicate the pressure applied to each surface from the gas 59. Thus, the gas pressure received by the anti-seal surface of the tip seal 51 is partially offset by the gas pressure introduced into the groove 60. However, since lubricating oil such as refrigerating machine oil is easily supplied to the sliding surface, the frictional force on the sliding surface can be greatly reduced as compared with the conventional product.

11 and 12, the opening 60c is provided on the inner peripheral surface 51b of the spiral, but may be provided on the outer peripheral surface 51a of the spiral.

In the chip seal of the second embodiment shown in FIGS. 7, 10, and 11, a groove is formed on the sliding surface, but a groove is formed on the anti-seal surface in addition to the sliding surface (seal surface). May be.

The chip seal of the present invention shown in the first embodiment and the second embodiment is preferably made of a synthetic resin. For example, polytetrafluoroethylene resin, polyphenylene sulfide (PPS) resin, polyether ether ketone (PEEK) ) Synthetic resins such as resins and liquid crystal polymers can be used. It can be set as the resin composition by mix | blending solid lubricants, such as fibrous fillers, such as carbon fiber and a whisker, tetrafluoroethylene resin powder, etc. with these synthetic resins. By using a PPS resin, a PEEK resin, or a liquid crystal polymer, it can be easily produced by injection molding.

The tip seal for the scroll compressor of the present invention can reduce the frictional force between the scroll member and the tip seal while maintaining the sealing performance, and can reduce the torque at the time of scrolling of the scroll member, so that it can be widely applied to the scroll compressor. .

1, 11, 31, 41, 51

Tip seal

2, 12, 32, 42, 52 Spiral winding

start end

3, 13, 33, 43, 53 Swirl

end winding end

4, 14

Recess

5, 15, 35 , 45, 55 Sliding

surface

6, 36, 56

Scroll substrate

7, 37, 57

Spiral wall

8, 38, 58

Gap

9, 39, 59

Gas

21, 61

Tip seal

22, 62

Compression chamber

23, 63

Seal groove

24, 64 Fixed

scroll

25, 65

Movable scroll

26, 66

Spiral wall boundary

40, 50, 60 Groove

Claims

In a scroll compressor including a fixed scroll and a movable scroll that are scroll members, a spiral chip seal for sealing a compression chamber formed between the fixed scroll and the movable scroll,
The tip seal has a plurality of recesses in which the sliding surface is partially cut out on a sliding surface with the scroll member, and the plurality of recesses are arranged on at least one of an inner peripheral surface and an outer peripheral surface of the spiral. Each of the recesses opens to the inner peripheral surface or the outer peripheral surface and does not penetrate the inner peripheral surface and the outer peripheral surface.
The scroll type according to claim 1, wherein the ratio of the total area of the recesses on the sliding surface (total area of the recesses / (total area of the recesses + actual sliding area) x 100) is 5 to 45%. Compressor tip seal.
2. The scroll-type compressor chip seal according to claim 1, wherein a planar shape of the concave portion is an arc shape or a substantially rectangular shape along a spiral shape.
2. The tip seal for a scroll compressor according to claim 1, wherein the depth of the recess is 45% or less of the thickness of the tip seal.
A plurality of the recesses are provided on the sliding surface so as to be spaced apart from each other in the length direction from the winding start end portion to the winding end end portion of the spiral of the chip seal. 1-20% of the unfolded length of the seal,
2. The scroll-type compressor tip seal according to claim 1, wherein a space between adjacent recesses is a part of the sliding surface.
6. The scroll-type compressor tip seal according to claim 5, wherein the area of the planar shape of the recess is substantially the same between the recesses.
The scroll-type compressor tip seal according to claim 1, wherein a plurality of the recesses are provided at equal intervals on the sliding surface.
The planar shape of the concave portion is an arc shape, and the arc radius of the concave portion is continuously or stepwise increased from the winding start end portion of the tip seal spiral toward the winding end end portion. 4. A tip seal for a scroll compressor according to claim 3.
A spiral chip seal for sealing a compression chamber formed between a fixed scroll and a movable scroll which are scroll members in a scroll compressor,
The tip seal has a groove at the center in the width direction of the tip seal at least on the sliding surface with the scroll member, and the groove is formed over substantially the entire length of the tip seal. Scroll type compressor tip seal.
10. The scroll-type compressor tip seal according to claim 9, wherein the groove width of the groove is 1/20 to 2/5 of the width dimension of the tip seal.
11. The scroll type compressor tip seal according to claim 10, wherein the groove width increases continuously or stepwise from a winding start end portion to a winding end end portion of the tip seal spiral.
10. The tip seal for a scroll compressor according to claim 9, wherein a groove depth of the groove is 35% or less of a thickness of the tip seal.
10. The scroll compressor tip seal according to claim 9, wherein the groove is provided with an opening connected to the groove on either the inner peripheral surface or the outer peripheral surface of the spiral.
The opening has a concave shape in which the sliding surface is cut out, and a plurality of the openings are provided apart from each other in the length direction from the winding start end to the winding end of the tip seal spiral. A tip seal for a scroll compressor according to claim 13.
2. The tip seal for a scroll compressor according to claim 1, wherein the tip seal is made of a synthetic resin.