JP2008248758A - Scroll type fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To eliminate troublesomeness dimension management of a seal member and improve seal performance of a sliding surface between a fixed scroll and a revolving scroll in a scroll type fluid machine. <P>SOLUTION: This scroll type compressor comprises the fixed scroll 01 including a base plate 4 and a scroll wall 1, and the revolving scroll 09 including the base plate 4 and the scroll wall 1, forming a scroll groove 2 on scroll wall end surfaces 1c of both of the scrolls along an extension directions of the scroll walls 1, and holding a seal member 3 touching the base plate 4 in each groove 2. A scroll groove is a penetration groove eliminating bulkhead in a scroll direction out of bulkheads constructing an inner end part and an outer end part, a wedge shape projection 5 is formed on both side wall surfaces of at least one section of the scroll groove 2, and the seal member 3 is compressed and retained by the wedge shape projection 5 while deforming a side surface of the seal member 3. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a sealing mechanism for ensuring the sealing performance of a compression chamber formed between spiral wall end surfaces of both scrolls in a scroll type fluid machine including a fixed scroll and a turning scroll, and the materials of the sealing members are different. Even in this case, the present invention relates to a scroll type fluid machine that can unify the dimensions of a seal member and prevent a decrease in the life of the seal member.

In the scroll compressor, a fixed scroll and a orbiting scroll each having a substrate and a spiral wall are meshed with each other by the spiral wall to form a compression chamber therebetween. Then, when the orbiting scroll revolves around the axis of the fixed scroll, the compression chamber moves to the center side and gas compression is performed.
And in order to ensure the sealing property of this compression chamber, the spiral surface of the scroll wall of the fixed scroll and the orbiting scroll is formed with a spiral groove along the extension direction of the spiral, and the spiral groove is opposed to the inside. A spiral seal member is formed that contacts the substrate of the counterpart scroll arranged to form a seal surface.

  Patent Document 1 (Japanese Patent Laid-Open No. 8-4670) discloses such a scroll compressor and its sealing mechanism. Hereinafter, the configuration of the scroll compressor disclosed in Patent Document 1 will be described with reference to FIGS. 6 and 7. FIG. 6 is a longitudinal sectional view of a conventional scroll compressor, FIG. 7 is an elevation view of the orbiting scroll of the scroll compressor, and FIG. 8A is a view of the spiral wall of the scroll compressor. It is a top view which shows an inner end part typically, (b) is CC sectional drawing in (a).

  In FIG. 6, a fixed scroll 01 made of aluminum also serves as a center housing, and a front housing 02 and a rear housing 03 are fixed to both front and rear end faces thereof. The rotating shaft 04 is rotatably supported in the front housing 02 by a bearing 05, and an eccentric shaft 06 projects from the inner end thereof. The bush 07 is rotatably supported by the eccentric shaft 06, and a bearing 08 is fitted on the outer periphery thereof.

  The orbiting scroll 09 made of aluminum is supported by the bush 07 via the bearing 08 so as to be relatively rotatable, and is prevented from rotating about its own axis by a known regulating mechanism 010. Then, when the rotary shaft 04 is rotated, the orbiting scroll 09 is revolved around the axis of the rotary shaft 04 via the bush 07 and the bearing 08 by the eccentric shaft 06.

  The fixed scroll 01 includes a substrate 011 and a spiral wall 012 that stands integrally on the inner peripheral surface thereof. Similarly, as shown in FIGS. 6 and 7, the orbiting scroll 09 also includes a substrate 013 and a spiral wall 014 that stands integrally on the inner peripheral surface thereof. The scrolls 01 and 09 are meshed with each other at the spiral walls 012 and 014, and the end surfaces in the axial direction of the spiral walls 012 and 014 are opposed to the substrates 011 and 013 of the scrolls 01 and 09 facing each other.

  The inner ends 024 of the spiral walls 012 and 014 are thicker than the other portions to ensure strength. The inner end edge 025 is formed in a substantially arc shape. The spiral grooves 015 and 016 are formed on the end surfaces of the spiral walls 012 and 014 of both scrolls 01 and 09 so as to extend in the direction of extension of the spiral shape, the inner end portion 026 is wide, and the inner end edge 027 is arcuate. Is formed. Spiral chip seals 017 and 018 as seal members are made of nylon resin and have a similar shape to the spiral grooves 015 and 016.

  Therefore, the inner ends 028 of the chip seals 017 and 018 are wide, and the inner ends 029 are formed in an arc shape. The tip seals 017 and 018 are accommodated in the respective spiral grooves 015 and 016 having the corresponding shapes, and as shown in FIG. 8B, the substrates 011 and 013 of the opposing scrolls 01 and 09 with the outer surfaces facing each other. Is in pressure contact. By this seal, a compression chamber r surrounded by the substrates 011 and 013 and the spiral walls 012 and 014 of both scrolls 01 and 09 is formed.

  The pressure receiving ring 030 is disposed between the orbiting scroll 09 and the front housing 02 and receives a compression reaction force acting on the orbiting scroll 09 in the axial direction thereof. The compression reaction force acting on the pressure receiving ring 030 is received by the front housing 02.

  As shown in FIG. 6, the suction chamber 019 is formed between the outer peripheral portions of the spiral walls 012 and 014 of the scrolls 01 and 09, and the refrigerant gas is sucked into the inside thereof. The discharge port 020 is formed in the substrate 011 of the fixed scroll 01 and communicates the compression chamber r with the discharge chamber 021 in the rear housing 03. The discharge valve 022 is disposed at the outer end of the discharge port 020, and its open position is regulated by the retainer 023.

  During operation of the compressor, the pressure in the compression chamber r between the scrolls 01 and 09 gradually increases as the spiral walls 012 and 014 move from the outer peripheral side to the center side. For this reason, the temperature on the center side increases, and the tip seals 017 and 018 and the spiral walls 012 and 014 are thermally expanded. The tip seals 017 and 018 are relatively expanded with respect to the spiral grooves 015 and 016 due to the difference in thermal expansion coefficient between the tip seals 017 and 018 made of nylon resin and the spiral walls 012 and 014 made of aluminum. . The thermal expansion amount of the tip seals 017 and 018 is larger in the spiral direction than in the width direction due to the spiral shape.

  In this compressor, in the gap between the tip seals 017 and 018 and the spiral grooves 015 and 016, the gaps s2 and s3 in the spiral direction are secured larger than the gap s1 in the width direction. The gaps s2 and s3 in the spiral direction have a larger outer end side gap s3 than the inner end side gap s2. As a result, even if the chip seals 017 and 018 expand during operation of the compressor, it is allowed to ensure that an appropriate gap is secured, and a reduction in the sealing function can be prevented.

  Further, in Patent Document 2 (Japanese Patent Laid-Open No. 55-81296), in a scroll compressor, a spiral groove is opened at the end face of the inner end of the spiral wall, and a part of the high-pressure fluid is introduced from the opening. It is disclosed that the sealing function is maintained by pressing the tip seal against the opposing scroll substrate with the high-pressure fluid.

In Patent Document 3 (Utility Model Registration No. 2551380), in a scroll compressor, a wedge-shaped protrusion is provided in a spiral groove formed on an end surface of a spiral wall, and a chip seal accommodated in the spiral groove is provided. A configuration is disclosed in which the tip seal can be prevented from moving in the spiral direction by being held with a wedge-shaped projection.
JP-A-8-4670 JP-A-55-81296 Utility Model Registration No. 2551380

  In the conventional scroll type fluid machine, as disclosed in Patent Document 1, a gap is provided between the spiral groove and the seal member accommodated in the spiral groove, and the inner end is compared with the gap in the width direction. The thermal expansion of the seal member can be absorbed by ensuring a large clearance in the spiral direction provided in the outer and outer end portions. The environment in which the scroll fluid machine is operated varies. For example, it may be exposed to radiation. In this case, the deterioration of the seal member becomes severe. For this reason, seal members of different materials are prepared according to different environments. For this reason, the various thermal expansion coefficients and elastic deformations of the various seal members are different, so the length of the seal member must be determined according to the material, processing dimensions are difficult to manage, and performance is stable. I did not.

  As in Patent Document 1, the conventional spiral groove has a closed wall at the inner end portion and the outer end portion, respectively. Accordingly, when all the dimensions of the seal member are the same, in the seal member having a large thermal expansion amount, there is no escape space for the seal member thermally expanded at the inner end portion or the outer end portion of the seal member. It deformed into a corrugated shape and strongly hits the opposing scroll substrate, which resulted in a reduction in the life of the seal member.

Further, since the inner end portion of the spiral groove is close to the center portion of the spiral wall, a fluid compressed to a high pressure is created. When this high-pressure fluid enters between the seal member and the bottom surface of the spiral groove, the pressure of the high-pressure fluid that has entered presses the seal member against the substrate of the opposing scroll that is disposed oppositely, and the sealing performance is improved. It works to improve.
However, in the conventional spiral groove, as shown in FIG. 8, since there is a closed wall 031 at the inner ends of the spiral grooves 015 and 016, the high-pressure fluid can be removed from the closed wall 031 as indicated by an arrow b. You have to go around the end face. For this reason, there is a problem in that the high-pressure fluid is prevented from entering between the seal member and the bottom surface of the spiral groove.

  In Patent Document 2, a spiral groove is opened on the end face of the inner wall of the spiral wall, and a part of the high-pressure fluid is introduced from the opening, whereby the tip seal is disposed on the opposite scroll arranged by the high-pressure fluid. Although it is disclosed to press against the substrate, the size of the opening is smaller than the width of the seal member, and therefore does not allow the seal member to expand due to thermal expansion. Therefore, also in Patent Document 2, the tip seal extended by thermal expansion is deformed by hitting the spiral groove, and is strongly hit by the substrate of the counterpart scroll, thereby reducing the life.

In view of the problems of the prior art, the present invention eliminates the troublesome size management of the seal member in the scroll type fluid machine, so even if the seal member material is different, all the seal members can be applied with the same size. Another object of the present invention is to realize a scroll fluid machine that does not cause a reduction in the service life of the seal member.
It is another object of the present invention to prevent the sealing performance of the sealing member from being impaired at the inner end and the outer end of the spiral groove.

In order to achieve such an object, the scroll type fluid machine of the present invention includes:
Each of the scrolls is composed of a fixed scroll and a orbiting scroll each having a substrate and a spiral wall standing on the substrate, and a substrate and a sealing surface of the counterpart scroll are formed in spiral grooves formed on the end surfaces of the scroll walls of both scrolls. In a scroll type fluid machine containing a seal member,
While removing the partition wall in the spiral direction from the partition walls constituting the inner end portion and the outer end portion of the spiral groove, and forming a through groove,
A restraining means for restraining the spiral movement of the seal member is provided in at least one location of the spiral groove.

In the device of the present invention, the amount of elongation due to thermal expansion, elastic deformation, etc. of the seal member is obtained by using a through groove that eliminates the partition in the spiral direction among the partition walls constituting the inner and outer ends of the spiral groove. Regardless, the inner end portion or the outer end portion of the seal member does not hit the partition wall of the spiral groove.
By adopting such a configuration, the seal member does not hit the partition wall of the spiral groove to be deformed, so that the life of the seal member is not reduced.
In the present invention, since it is not necessary to previously provide a gap in the spiral direction between the seal member and the spiral groove as in the prior art, sealing performance is not deteriorated due to the presence of the gap.

  Further, with this configuration, the fluid compressed to a high pressure at the inner end portion of the spiral groove can easily enter the gap between the bottom surface of the seal member and the spiral groove from the through portion of the spiral groove. When this high-pressure fluid enters the gap, the seal member is pressed against the substrate of the scroll disposed opposite to the seal member, and the sealing performance between the inner end and the substrate can be further improved.

  Further, in the device of the present invention, in order to fix the seal member in the spiral groove, a restraining means for restraining the movement of the seal member in the spiral direction is provided at at least one location of the spiral groove. Accordingly, the seal member can be prevented from moving in the spiral direction, and the seal member can be fixed to the spiral groove.

  In the apparatus of the present invention, the restraining means may be configured to form wedge-shaped protrusions on both side wall surfaces of the spiral groove, and hold the seal member with pressure while deforming the side surfaces of the seal member with the wedge-shaped protrusions. . The wedge-shaped protrusion is used to hold the seal member while deforming the side surface of the seal member. As a result, the seal member can be prevented from shifting in the spiral direction.

  Further, in the device of the present invention, when the compressibility of the fluid to be compressed of the scroll type fluid machine is high, the staircase is stepped through a step portion provided at least at one place from the center to the periphery of the bottom surface of the spiral groove. The seal member is separated for each bottom surface having a different height of the spiral groove, and one end of each seal member is removed except for the seal member accommodated in the outermost peripheral portion of the spiral groove. It is preferable that the position in the spiral direction is fixed against the stepped wall of the stepped portion, and the restraining means is provided in a spiral groove that accommodates the outermost peripheral seal member.

  With this configuration, since the seal member is divided into a plurality along the spiral direction, the movement of each seal member is facilitated. Therefore, in the vicinity of the inner end portion of the spiral groove, the high pressure fluid that has entered between the seal member and the spiral groove is likely to be pressed against the scroll substrate on which the seal member is opposed, and the seal in the vicinity of the inner end portion. The performance can be further improved.

  Further, since the pressure of the compressed fluid is higher in the central portion than in the peripheral portion of the spiral wall, the pressure of the compressed fluid from the central portion toward the peripheral portion is applied to the seal member accommodated in the spiral groove. Therefore, each seal member does not move to the center side. On the other hand, since the seal member excluding the seal member arranged at the outermost peripheral part in the spiral direction has a stepped wall of the stepped part on the peripheral side, the position in the spiral direction within the spiral groove by hitting the stepped wall The restraint is held.

As described above, the seal member excluding the seal member arranged at the outermost peripheral part in the spiral direction uses the pressurizing force by the high-pressure fluid on the center side and the step part, and does not use any special restraining means. The position of the seal member in the spiral direction can be restricted.
In addition, it is necessary to provide a restraining means separately with respect to the sealing member arrange | positioned in the spiral direction outermost periphery part. The restraining means may be configured such that the wedge-shaped protrusion is provided in a spiral groove. Further, depending on the operating conditions of the scroll type fluid machine, it is necessary to firmly hold the seal member in the spiral groove. In that case, you may provide a restraining means also in sealing members other than a spiral direction outermost periphery part.

  According to the apparatus of the present invention, the partition in the spiral direction is removed from the partition walls forming the inner and outer ends of the spiral groove formed on the end surface of the spiral wall to form a through groove, and the spiral groove By providing a restraining means for restraining the movement of the seal member in the spiral direction at at least one location of the seal member, even if the seal member is thermally expanded, the seal member hits the partition wall of the spiral groove at the inner end portion or the outer end portion. And will not be deformed. For this reason, the lifetime of the seal member is not reduced, and it is not necessary to change the length of the seal member for each type of material of the seal member, so that the dimension management of the seal member is facilitated.

  In addition, since it is not necessary to provide a gap that allows for thermal expansion and elastic deformation of the seal member at the inner and outer ends of the spiral groove, it is possible to prevent deterioration of the sealing performance at the inner and outer ends. Can do. Further, since the high-pressure fluid easily enters between the seal member and the bottom surface of the spiral groove at the inner end portion of the spiral groove, the sealing performance between the seal member and the scroll substrate disposed opposite to the seal member. Can be further improved.

Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the scope of the present invention to that unless otherwise specified.
(Embodiment 1)

  Next, a first embodiment in which the present invention is applied to a scroll compressor will be described with reference to FIGS. FIG. 1 is a plan view showing a spiral wall and a tip seal according to the present embodiment, FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1, and FIG. 3 shows a groove processing procedure of the spiral wall end face. (A) is an elevational sectional view, (b) is a plan view.

  1 and 2, a spiral wall 1 is erected in the axial direction with respect to a substrate (not shown) constituting a fixed scroll or a turning scroll of a scroll compressor. As shown in FIG. 2, the substrate 4 of the counterpart scroll is disposed so as to face the end surface 1 c of the spiral wall 1. A spiral groove 2 having a rectangular cross section is formed along the spiral direction on an end surface 1c of the spiral wall 1 where the spiral wall 1 forms a seal with the counterpart substrate 4. A chip seal 3 made of a strip-shaped resin, for example, a nylon resin, is accommodated in the spiral groove 2, and the upper surface of the chip seal 3 is pressed against the substrate 4 to form a seal portion.

The inner end portion 1a of the spiral wall 1 and the inner end portion 3a of the chip seal 3 are cut in a direction perpendicular to the spiral direction, and the spiral groove 2 has a penetrating groove shape without a closing wall. This configuration is the same for the outer end portion 1 b of the spiral wall 1 and the outer end portion 3 b of the tip seal 3. Further, the spiral wall 1 is provided with a wedge-shaped protrusion 5 that protrudes inward from both side surfaces of the spiral groove 2 in the vicinity of the center of the spiral wall 1 in the spiral direction.
The wedge-shaped protrusion 5 is for preventing the tip seal 3 accommodated in the spiral groove 2 from moving in the spiral direction and fixing it to the spiral groove 2. The chip seal 3 is formed of a self-lubricating resin material having a width slightly smaller than that of the spiral groove 2 without providing a concave portion corresponding to the wedge-shaped protrusion 5.

  The chip seal 3 is held with pressure while being deformed by the wedge-shaped protrusion 5. It is determined according to the amount of thermal contraction and the amount of elastic deformation whether the degree of deformation of the tip seal 3 should be kept within the range of elastic deformation or to be deformed until it is plastically deformed. A processing procedure for forming the wedge-shaped projection 5 will be described below with reference to FIG. The wedge-shaped projections 5 do not need to be formed using a special tool, and can be easily processed by devising the feeding direction during end mill processing for forming the spiral groove 2.

  In FIG. 3, the end mill tool 9 is lifted upward at a point D in the middle thereof, and is then fed forward, then cut downward at the point E, and fed again to shift the spiral direction by a distance T. A pair of wedge-shaped projections 5 sandwiched between two virtual circles R are formed. In this case, the tops 5a of the pair of wedge-shaped projections 5 must be separated from each other. For this purpose, the pre-feed distance T is smaller than the groove width S of the spiral groove 2, in other words, defined by the end mill tool 9. It is necessary to set it to be smaller than the diameter length of the two virtual circles R. The protrusion width T is determined by the adiabatic compression amount in the center region and the material and thickness of the tip seal 3.

  The tip seal 3 is formed with a width slightly smaller than the groove width of the spiral groove 2 in consideration of thermal expansion, and is opposed to the other side scroll with its height slightly larger than the height of the spiral groove 2. The substrate 4 is configured so as to be smoothly press-contactable. Since the tip seal 3 is a soft material made of a self-lubricating resin, the tip end of the tip seal 3 is matched with the start end of the spiral groove 2 and press-fitted into the spiral groove 2. As a result, the tip seal 3 is fitted into the spiral groove 2 while being plastically deformed and elastically deformed at the wedge-shaped protrusion 5, so that the chip seal 3 can be held and pressed by the wedge-shaped protrusion 5.

  Note that the protrusion width T may be set so that it can be firmly held within a range where it cannot be pulled out by the tensile force of heat shrinkage and is not extracted, and the protrusion width T depends on the adiabatic compression amount in the center region and the material and thickness of the tip seal 3. Determined arbitrarily.

  According to the present embodiment having such a configuration, the inner end 3a or the outer end of the tip seal 3 has no closed wall at the inner end and the outer end of the spiral groove 2 and has a through groove shape. Even if 3b thermally expands, it does not hit the partition wall of the spiral groove 2. Therefore, the inner end portion 3a or the outer end portion 3b of the chip seal 3 is not deformed, so that the lifetime is not reduced. Further, it is not necessary to change the size of the tip seal 3 for each material of the tip seal 3, and the size management of the tip seal 3 is facilitated.

  Further, since it is not necessary to provide a gap in the spiral direction in advance in consideration of the thermal expansion amount of the chip seal 3 at the inner end portion and the outer end portion of the spiral groove 2, the sealing performance at the inner end portion and the outer end portion is improved. Deterioration can be prevented. Further, since the closed wall is eliminated at the inner end of the spiral groove 2, the high-pressure fluid can easily enter between the tip seal 3 and the bottom surface of the spiral groove 2 as indicated by an arrow a in FIG. 2. Since the chip seal 3 is pressed toward the substrate 4 disposed opposite to the high pressure fluid, the sealing performance between the chip seal 3 and the substrate 4 can be further improved.

  Further, when the chip seal 3 made of a self-lubricating resin is press-fitted into the spiral groove 2, the chip seal 3 is inserted while causing plastic deformation or elastic deformation using the wedge-shaped projections 5, so that the processing accuracy is slightly increased. Even if there is a deviation, it can be pinched and held with high accuracy by the elastic force of the tip seal 3. In addition, since the tip seal 3 is held by the wedge-shaped protrusion 5, even if a tensile force of the chip seal 3 is applied to the wedge-shaped protrusion 5 due to thermal contraction of the chip seal 3, the chip seal 3 is not displaced and the accuracy is increased. The position can be maintained well.

  As a result, smooth sealing performance can be ensured, and since the strength of the tip seal 3 can be maintained over a long period without causing uneven wear, the durability of the tip seal 3 is improved. Further, it is not necessary to process the tip seal 3 in advance, and the wedge-shaped projection 5 can be easily processed only by changing the feed direction of the end mill tool 9 when the spiral groove 2 is processed.

  Further, when assembling the tip seal 3, it is only necessary to press-fit the tip seal 3 into the spiral groove 2 provided with the wedge-shaped projections 5 while keeping the tip seal 3 in the form of a band and having the start end matched with the end of the spiral groove 2. Since the tip seal 3 is formed with a width slightly smaller than the width of the spiral groove 2, it may be inserted into the spiral groove 2, while completely retaining and holding the tension in the longitudinal direction of the starting end. And easy to assemble.

As an example, a Teflon (registered trademark) tip seal A (thermal expansion coefficient: 16.0 × 10 ⁻⁵ (1 / ° C.)) is used as a tip seal under a normal temperature environment, and the Teflon under a high temperature environment. (Registered trademark) type chip seal B (thermal expansion coefficient: 5.0 × 10 ⁻⁵ (1 / ° C.)), and the material of the spiral wall is aluminum (thermal expansion coefficient: 2.3 × 10 ⁻⁵ (1 / C)), the Teflon (registered trademark) tip seal A is 8 times that of aluminum, and the Teflon (registered trademark) tip seal B is twice that of aluminum. Accordingly, the difference in thermal expansion between the tip seal and the aluminum spiral wall is large, and in the conventional method, it is necessary to provide a gap in the spiral direction at the inner end and the outer end of the spiral groove 2. It can be seen that the sealing performance deteriorates at the inner end and the outer end due to the presence of.
(Embodiment 2)

  Next, a second embodiment of the present invention will be described with reference to FIGS. 4 is a plan view showing the spiral wall and the tip seal of this embodiment, and FIG. 5 is a cross-sectional view taken along line BB in FIG. 4 and 5, in the present embodiment, the height of the bottom surface of the spiral groove 12 formed in the end surface 11c of the spiral wall 11 is such that the stepped portion 17 is a boundary between the inner end portion 11a side and the outer end portion 11b side. As configured differently. That is, the bottom surface 12d of the spiral groove 12 on the inner end portion 11a side is configured to be lower by the height of the stepped portion 17 than the bottom surface 12e on the outer end portion 11b side.

  In the spiral groove 2 having a low bottom surface 12d and extending from the inner end portion 11a to the stepped portion 17, a tip seal 13 having a height that is larger by the height of the stepped portion 17 is fitted into the spiral groove 2. ing. Further, in the spiral groove 2 having the shallow bottom surface 12 e from the outer end portion 11 b to the stepped portion 17, a tip seal 16 having a height dimension smaller than the tip seal 13 by the height of the stepped portion 17 is swirled. It is inserted in the groove 2. The heights of the upper surfaces of the chip seal 13 and the chip seal 16 in contact with the substrate 14 are the same. The spiral groove 2 in which the chip seal 16 is inserted is provided with a wedge-shaped projection 15 having the same configuration as the wedge-shaped projection 5 of the first embodiment.

  In the present embodiment, the operational effects obtained by the first embodiment, that is, the prevention of the life reduction due to the elimination of deformation at the time of thermal expansion of the chip seals 13 and 16, and the inner end portion 11a and the outer portion of the spiral wall 11 are prevented. It is possible to improve the sealing performance between the chip seals 13 and 16 and the substrate 14 by not providing a gap between the chip seal and the spiral groove 12 in the end portion 11b in advance, and further, the following operational effects. Can be newly obtained.

  In other words, since the tip seal is divided into the tip seal 13 and the tip seal 16 with the stepped portion 17 as a boundary, the high-pressure fluid on the center side of the spiral wall 11 causes the bottom surface of the tip seal 13 and the bottom surface 12d of the spiral groove 2 to be formed. Therefore, the sealing performance between the chip seal 13 and the substrate 14 can be improved by easily pressing the chip seal 13 against the substrate 14.

  Further, the tip seal 13 receives pressure from the central portion toward the peripheral portion due to the pressure of the high-pressure fluid, and the tip seal 13 that has received such pressure is pressed against the step wall of the step portion 17. By such simple means, the tip seal 13 is restrained from moving in both the central direction and the peripheral direction, so that no special means for restraining the tip seal 13 from moving in the spiral direction is required. Further, the tip seal 16 is held by the wedge-shaped protrusion 5 so that the movement in the spiral direction is restricted.

  According to the present invention, in the scroll type fluid machine, it is possible to easily manage the size of the seal member that seals the sliding surface between the fixed scroll and the orbiting scroll, and to improve the sealing performance of the sliding surface with a simple configuration. be able to.

It is a top view which shows the spiral wall and chip | tip seal | sticker of 1st Embodiment of this invention. It is sectional drawing which follows the AA line in FIG. The groove part processing procedure of the spiral wall end surface of the said 1st Embodiment is shown, (a) is an elevation sectional drawing, (b) is a top view. It is a top view which shows the spiral wall and chip | tip seal | sticker of 2nd Embodiment of this invention. It is sectional drawing which follows the BB line in FIG. It is a longitudinal cross-sectional view of the conventional scroll type compressor. It is an elevation view of the orbiting scroll of the conventional scroll type compressor. (A) is a top view which shows typically the inner edge part of the spiral wall of the conventional scroll compressor, (b) is CC sectional drawing in (a).

Explanation of symbols

01 fixed scroll 09 orbiting scroll 1,11 spiral wall 1a, 3a, 11a, 13a inner end 1b, 3b, 11b, 13b outer end 2,12 spiral groove 3,13,16 chip seal (seal member)
4,14 Substrate 5,15 Wedge projection 17 Stepped portion

Claims (2)

Each of the scrolls is composed of a fixed scroll and a orbiting scroll each having a substrate and a spiral wall standing on the substrate, and a substrate and a sealing surface of the counterpart scroll are formed in spiral grooves formed on the end surfaces of the scroll walls of both scrolls. In a scroll type fluid machine containing a seal member,
While removing the partition wall in the spiral direction from the partition walls constituting the inner end portion and the outer end portion of the spiral groove, and forming a through groove,
A scroll type fluid machine characterized in that a constraining means for constraining the spiral movement of the seal member is provided in at least one portion of the spiral groove.   The constraining means is configured such that wedge-shaped projections are formed on both side walls of the spiral groove, and the seal member is clamped and held while the side surfaces of the seal member are deformed by the wedge-shaped projections. Item 2. The scroll fluid machine according to Item 1.

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