JP2018071359A - Scroll fluid machine - Google Patents

Abstract

The present invention provides a scroll fluid machine that reduces the sliding area of a center-side tip seal where a large surface pressure is generated and enables sliding loss, that is, power reduction, while ensuring compression performance. For the purpose.
The first scroll includes a first scroll having an end plate and a wrap portion, and a second scroll having the end plate and the wrap portion and facing the first scroll. And a groove on the face of the end plate facing the wrap portion of the second scroll, and a tip seal that seals between the first scroll and the second scroll in the seal groove, In at least one of the first scroll and the second scroll, there is provided a scroll fluid machine in which the radial width dimension on the center side of the tip seal and the seal groove is smaller than the radial width dimension on the outer peripheral side. .
[Selection] Figure 2

Description

  The present invention relates to a scroll type fluid machine.

  As background art of the present invention, there are Patent Document 1 and Patent Document 2. Patent Document 1 states that “the tip seal 50 has a constant width dimension in the spiral direction, and a width dimension of the groove portion 13 of the central portion 17b of the movable tooth portion 11b is constant in the spiral direction. A scroll type compressor is described in which the width dimension of the groove portion 13 of the portion 17a is smaller than the width dimension Wb of the groove portion 13 of the central side portion 17b of the movable tooth portion 11b. Patent Document 2 states that “the concave groove portion 25 and the tip seal 26 during assembly gradually increase the clearance between them from the spiral outer peripheral portion of the scroll side plate portion 23 toward the spiral central portion of the scroll substrate portion. The dimension of the seal member according to either the direction of the rotation axis and the direction parallel to the facing surface of the scroll substrate portion or the direction of the rotation axis of the scroll substrate portion or the direction parallel to the facing surface of the scroll substrate portion is The scroll compressor is set to be gradually smaller from the spiral outer peripheral portion of the scroll side plate portion toward the spiral central portion.

JP 2010-196688 A JP-A-6-235386

  In Patent Document 1, the width dimension of the tip seal is constant over the spiral direction, while the width dimension of the center side portion of the groove portion 13 (tip seal groove formed in the wrap portion of the orbiting scroll) of the movable tooth portion 11b. Is larger than the width of the outer periphery.

  Moreover, in patent document 2, the clearance between the concave groove part 25 and the chip seal 26 is gradually increased from the spiral outer peripheral part toward the spiral central part. Further, the width dimension of the seal member (chip seal) gradually decreases from the spiral outer peripheral portion toward the spiral central portion from the spiral outer peripheral portion of the scroll side plate portion 23 toward the spiral central portion.

  However, in the case of Patent Document 1 and Patent Document 2, by increasing the clearance between the tip seal and the groove on the spiral inner peripheral side, the fluid leaks until the tip seal is thermally expanded to an appropriate size. It becomes difficult to secure compression performance.

  In view of the above problems, the present invention reduces the sliding area of the center side chip seal where a large surface pressure is generated, enables sliding loss, that is, power reduction, while ensuring the compression performance. The purpose is to provide.

  In order to solve the above-mentioned problem, the present invention includes a first scroll having an end plate and a wrap portion, and a second scroll having the end plate and the wrap portion and facing the first scroll, A chip having a seal groove on the opposite end plate side surfaces of the first scroll and the second scroll lap, and sealing between the first scroll and the second scroll in the seal groove A scroll type having a seal and having a radial width dimension on the center side of the tip seal and the seal groove smaller than a radial width dimension on the outer peripheral side in at least one of the first scroll and the second scroll Provide a fluid machine.

  According to the present invention, it is possible to provide a scroll fluid machine that can reduce power while ensuring compression performance.

It is sectional drawing of the scroll type fluid machine which concerns on the Example of this invention. It is a perspective view of a turning scroll and a tip seal concerning an example of the present invention. It is sectional drawing of the turning scroll and chip seal which concern on the Example of this invention. It is the M section enlarged view of FIG. It is sectional drawing of the scroll wrap front-end | tip part which concerns on the Example of this invention. It is the figure which described the other party scroll tooth bottom in FIG. It is a perspective view of a turning scroll and a tip seal concerning a modification of the present invention. It is an enlarged view of a turning scroll and a tip seal concerning a modification of the present invention.

  Hereinafter, a scroll type air compressor as an example of a scroll type fluid machine according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

  An embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a cross-sectional view of a scroll compressor according to this embodiment. The casing 1 of the scroll type air compressor is formed in a cylindrical shape, is provided outside the orbiting scroll 8, and supports the drive shaft 15 in a rotatable manner.

  As shown in FIG. 1, the fixed scroll 2 provided on the opening side of the casing 1 has an end plate 3 formed in a substantially disc shape with an axis OO as a center, and a shaft on a tooth bottom surface serving as a surface of the end plate 3. A spiral wrap portion 4 erected in the direction, a cylindrical outer peripheral wall portion 5 that surrounds the wrap portion 4 and is provided on the outer diameter side of the end plate 3, and a plurality of projections that protrude from the rear surface of the end plate 3 The cooling fins 6 are generally configured.

  Here, the wrap portion 4 is wound, for example, in a spiral shape of about 4 turns from the radially inner side to the radially outer side when the outermost diameter end is the winding start end and the outermost diameter end is the winding end end, for example. It has been turned. The tooth tip surface of the wrap portion 4 is separated from the tooth bottom surface of the end plate 9 of the orbiting scroll 8 as a counterpart by a predetermined axial dimension.

  In addition, seal grooves 4A and 4B are provided along the winding direction of the wrap portion 4 on the tooth tip surface of the wrap portion 4 (the surface on the side facing the end plate 9 of the other turning scroll 8). In 4A and 4B, chip seals 7A and 7B are provided as seal members in sliding contact with the end plate 9 of the orbiting scroll 8. Furthermore, the outer peripheral wall 5 has a substantially circular shape. And the outer peripheral wall part 5 is arrange | positioned in the radial direction outer side rather than the lap | wrap part 10 in order to avoid interference with the lap | wrap part 10 of the turning scroll 8. FIG.

  The orbiting scroll 8 provided so as to be able to orbit inside the casing 1 in the radial direction stands on a substantially disc-shaped end plate 9 disposed opposite to the end plate 3 of the fixed scroll 2 and a tooth bottom surface that becomes the surface of the end plate 9. The spiral wrap portion 10 provided and a plurality of cooling fins 11 projecting from the back surface of the end plate 9 are generally configured. A rear plate 12 connected to the drive shaft 15 is provided on the front end side of the cooling fin 11.

  Here, the wrap portion 10 has, for example, a spiral shape of about 3 turns from the radially inner side to the radially outer side, almost similar to the wrap portion 4 of the fixed scroll 2. The tooth tip surface of the wrap portion 10 is separated from the tooth bottom surface of the end plate 3 of the fixed scroll 2 which is the counterpart by a predetermined axial dimension. In addition, seal grooves 10A and 10B are provided along the winding direction of the wrap portion 10 on the tooth tip surface of the wrap portion 10 (the surface facing the end plate 3 of the fixed scroll 2 on the other side). In 10A and 10B, chip seals 13A and 13B are provided as seal members that are in sliding contact with the end plate 3 of the fixed scroll 2.

  In addition, a cylindrical boss portion 14 that is connected to the crank portion 15A of the drive shaft 15 via a swivel bearing 14a and a bearing housing 14b is integrally formed on the center side of the back plate 12. At this time, a pulley 15B is provided on one end side of the drive shaft 15 outside the casing 1, and this pulley 15B is, for example, a belt (not shown) on the output side of an electric motor as a drive source. And so on. As a result, the drive shaft 15 is rotationally driven by an electric motor or the like to cause the orbiting scroll 8 to orbit with respect to the fixed scroll 2. In this embodiment, the drive shaft 15 and the drive shaft of the electric motor are described as an example. However, the drive shaft 15 is used as the drive shaft of the electric motor, and is eccentric to the tip of the drive shaft of the electric motor. The crank portion 15 </ b> A may be formed, and the crank portion 15 </ b> A may be connected to the back plate 12.

  A cooling fan 16 is attached to the pulley 15B using bolts or the like, and the cooling fan 16 generates cooling air in the fan casing 17. As a result, the cooling fan 16 blows cooling air along the ducts in the fan casing 17 to the inside of the casing 1 and the back side of the scrolls 2, 8 to cool the casing 1, the fixed scroll 2, the orbiting scroll 8, etc. To do.

  Furthermore, between the back plate 12 and the casing 1, for example, three auxiliary cranks 18 (only one is shown) are provided as anti-rotation mechanisms for preventing the orbiting scroll 8 from rotating. The auxiliary crank 18 is disposed in an auxiliary crank boss portion 18b formed on the casing 1 and the back plate 12 via an auxiliary crank bearing 18a.

  A plurality of compression chambers 19 provided between the fixed scroll 2 and the orbiting scroll 8 are located between the wrap portions 4 and 10 and are sequentially formed from the radially outer side to the radially inner side to insert the tip seals 7A, 7B, Airtightly held by 13A and 13B. The compression chambers 19 are continuously reduced between the wrap portions 4 and 10 while moving from the radially outer side toward the radially inner side when the orbiting scroll 8 orbits in the forward direction. The

  Thereby, outside air is sucked into the compression chamber 19A located on the radially outer side of each compression chamber 19 from the suction port 20 described later, and this air reaches the compression chamber 19B located on the radially inner side. Compressed air becomes compressed air. The compressed air is discharged from the discharge port 22 and stored in an external storage tank (not shown).

  A suction port 20 provided on the outer diameter side of the fixed scroll 2 opens from the outer diameter side of the end plate 3 to the outer peripheral wall portion 5 and communicates with a compression chamber 19A located on the radially outer side. Further, the suction port 20 is located outside the end plate 3 of the fixed scroll 2 in the radial direction of the wrap portion 10 of the orbiting scroll 8 and opens in a range (non-sliding region) where the tip seal 13B does not slide. . And the suction inlet 20 sucks air in the compression chamber 19A located in the radial direction outer side through the suction filter 21, for example.

  The suction port 20 may be configured to suck in pressurized air. In this case, it is good also as a structure which removes the suction filter 21 and connects the suction inlet 20 to piping to which pressurized air is supplied.

  A discharge port 22 provided on the radially inner side (center side) of the end plate 3 of the fixed scroll 2 communicates with a compression chamber 19B located on the radially inner side, and discharges compressed air in the compression chamber 19B to the outside. It is.

  The flange 24 positioned radially outward from the lap portion 4 of the fixed scroll 2 fixes the fixed scroll 2 to the casing 1 with the flange 1 a portion of the casing 1. The positioning between the fixed scroll 2 and the casing 1 is performed by inserting a positioning member through the positioning hole 37.

  The face seal groove 25 provided on the end surface (flange 24) of the fixed scroll 2 facing the end plate 9 of the orbiting scroll 8 is located on the outer side in the radial direction of the outer peripheral wall portion 5 and has an annular shape surrounding the outer peripheral wall portion 5. Is formed. An annular face seal 26 is attached in the face seal groove 25. The face seal 26 hermetically seals between the end face (flange 24) of the fixed scroll 2 and the end plate 9 of the orbiting scroll 8, and prevents dust and the like from entering the outer peripheral wall portion 5 from between these. doing.

  The scroll type air compressor according to this embodiment has the above-described configuration. Next, the operation of the scroll type air compressor will be described.

  First, when the drive shaft 15 is rotationally driven by a drive source (not shown) such as an electric motor, the orbiting scroll 8 is centered on the axis OO of the drive shaft 15 in a state where the rotation is prevented by the rotation prevention mechanism. By performing the orbiting motion, the compression chamber 19 defined between the lap portion 4 of the fixed scroll 2 and the lap portion 10 of the orbiting scroll 8 is continuously reduced. Thereby, the air sucked from the suction port 20 of the fixed scroll 2 can be discharged toward the external tank (not shown) as compressed air from the discharge port 22 of the fixed scroll 2 while being sequentially compressed in each compression chamber 19. it can.

  The cooling structure of the scroll type air compressor according to this embodiment will be described. The cooling air generated by the cooling fan 16 circulates inside the casing 1 along the ducts in the fan casing 17 and the back side of the fixed scroll 2 and the orbiting scroll 8, and the casing 1, the fixed scroll 2, and the orbiting scroll 8 Cool etc.

  A detailed configuration of the chip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B in this embodiment will be described with reference to FIGS.

  2, 3, and 4 show the wrap portion 10 of the orbiting scroll 8 and seal grooves 10 </ b> A and 10 </ b> B and tip seals 13 </ b> A and 13 </ b> B provided at the tip thereof (only the orbiting scroll 8 side is shown, but the fixed scroll 2 The side is the same). The tip seals 13A and 13B are composed of a central side 13A including the innermost end and an outer peripheral side 13B including the outermost end. At the same time, the radial width dimension: t of the center side chip seal 13A is configured to be smaller than the radial width dimension: T of the outer side chip seal 13B (FIG. 5). Also, the seal grooves 10A and 10B into which the chip seals 13A and 13B are inserted are composed of a center side 10A and an outer peripheral side 10B in the same manner as the chip seal so as to match the width of the chip seal. It is configured to be smaller than the width dimension on the side.

  In this embodiment, the radial width dimensions of the chip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B are changed in two steps in a stepwise manner. The radial width dimensions of the tip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B may be changed in three or more steps. Further, the radial width dimensions of the chip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B may be changed continuously instead of stepwise. In these cases, at least the radial width dimension of the end portion on the center side of the chip seal and the seal groove is configured to be smaller than the radial width dimension of the end portion on the outer peripheral side.

  More than the case where the radial width dimension of the tip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B is changed in two steps in a stepped manner by continuously changing the radial width dimension. It is possible to reduce the shaft power of the compressor and improve the performance of the compressor.

  Further, the radial width dimension of the center-side seal groove 10A is configured to be smaller than the radial width dimension T of the outer peripheral chip seal 13B. Accordingly, when the chip seals 13A and 13B are mounted in the seal grooves 10A and 10B, the outer peripheral chip seal 13B does not enter the center side seal groove 10A. Therefore, the tip seals 13A and 13B can be easily and accurately mounted in the seal grooves 10A and 10B by pressing the interface between the center side and the outer periphery of the chip seals 13A and 13B against the boundary surfaces of the seal grooves 10A and 10B. Can do.

  Here, while the air sucked from the suction port 20 of the fixed scroll 2 is sequentially compressed in the compression chambers 19, a part of the air is directed to the discharge port 22 of the fixed scroll 2, and some of the tips are 7 A, 7 B, 13 A, 13 B. The back surface (the surface facing the seal grooves 4A, 4B, 10A, 10B) is pressed to act to seal the mating surfaces (end plates 3, 9). Since the back pressure increases toward the center of the compression chamber, the tip seals 7A and 13A on the center side receive a larger surface pressure than the tip seals 7B and 13B on the outer peripheral side. Therefore, when the width of the chip seal is constant from the center side to the outer peripheral side, the pressing load of the chip seal becomes strong on the center side. At this time, sliding loss increases due to an increase in frictional force at the sliding portion between the tip seal and the end plate on the center side.

  The tip seal pressing load due to the back pressure is reduced when the seal sliding area is reduced, and the frictional force is reduced to reduce the sliding loss. Therefore, the shaft power of the compressor can be reduced. In this embodiment, the radial width dimension of the center side chip seals 7A and 13A is made smaller than the radial width dimension of the outer periphery side chip seals 7B and 13B, thereby reducing the shaft power of the compressor.

  Further, since the sliding loss is reduced, the amount of heat generation is also reduced. In particular, the temperature of the sliding surfaces of the tip side chip seals 7A and 13A can be reduced, so that the life and reliability of the tip seals 7A, 7B, 13A and 13B are increased. Can be improved.

  Furthermore, since the volume is reduced by reducing the width of the center-side chip seals 7A and 13A, the material cost can be reduced and the cost can be reduced.

  On the other hand, since the tip seals 7B and 13B on the outer peripheral side are low in pressure, it is difficult to receive back pressure, and the pressing load on the mating surface is small. Therefore, it is desirable to make the pressure receiving area large in order to ensure sealing performance. In this embodiment, since the outer side chip seals 7B and 13B are made larger in the width direction than the center side chip seals 7A and 13A, the discharge performance (discharge) Air volume) can be maintained.

  As described above, according to this embodiment, the sliding loss of the chip seals 7A, 7B, 13A, and 13B can be reduced, and the sliding temperature can be reduced, so that the performance and reliability of the compressor can be improved. Furthermore, since the volume of the chip seal can be reduced, the cost can be reduced, and the machining area (processing time) can be reduced because the machining area is reduced.

  6 and 7 illustrate the detailed configuration of the tip seals 7A, 7B, 13A, 13B and the seal grooves 4A, 4B, 10A, 10B according to a modification of the present embodiment. 6 and 7 show the wrap portion 10 of the orbiting scroll 8 in this embodiment, the seal grooves 10A and 10B and the tip seals 13A and 13B provided at the tip (only the orbiting scroll 8 side is shown, but the fixed scroll 2 side is also shown. The same).

  In the modification, the tip seals 7A and 13A on the center side and the tip seals 7B and 13B on the outer peripheral side are formed separately. This makes it easier to process and attach to the seal grooves 4A, 4B, 10A, and 10B than to integrally form the center-side chip seals 7A and 13A and the outer peripheral side chip seals 7B and 13B. Can do. Moreover, since the processing and the mounting to the seal grooves 4A, 4B, 10A, and 10B can be performed with high accuracy, the sealing performance of the compressor can be further improved.

  In the present embodiment, the case where the present invention is applied to a scroll type air compressor as a scroll type fluid machine has been described as an example. However, the present invention is not limited to this, and the present invention is not limited to this. You may apply to a scroll type fluid machine. Moreover, you may apply to systems, such as a tank integrated package compressor provided with the scroll-type fluid machine, and a nitrogen gas generator.

  The embodiments described so far are merely examples of implementation in carrying out the present invention, and the technical scope of the present invention is not limitedly interpreted by these. That is, the present invention can be implemented in various forms without departing from the technical idea or the main features thereof.

DESCRIPTION OF SYMBOLS 1 Casing 1a Flange 2 Fixed scroll 3,9 End plate 4,10 Lapping part 4A, 4B, 10A, 10B Seal groove 5 Outer wall part 6,11 Cooling fin 7A, 7B, 13A, 13B Tip seal 8 Orbiting scroll 12 Back plate 14 Boss portion 14a Slewing bearing 14b Bearing housing 15 Drive shaft 15A Crank portion 15B Pulley 16 Cooling fan 17 Fan casing 18 Auxiliary crank 18a Auxiliary crank bearing 18b Auxiliary crank boss portion 19 Compression chamber 19A Compression chamber 19B Compression chamber 20 Suction port 21 Suction filter 22 Discharge port 24 Flange 25 Face seal groove 26 Face seal 37 Positioning hole 40 Auxiliary crank bearing 41 Bolt

Claims (8)

A first scroll having an end plate and a wrap portion;
A second scroll having an end plate and a wrap portion and facing the first scroll;
A seal groove on the end plate side surface of the scroll facing the first scroll and the second scroll wrap portion;
A chip seal that seals between the first scroll and the second scroll in the seal groove;
In at least one of the first scroll and the second scroll, the radial width dimension of the end portion on the center side of the tip seal and the seal groove is smaller than the radial width dimension of the end portion on the outer peripheral side. Scroll type fluid machine.   The radial width dimension continuously changes from the center side to the outer peripheral side of the tip seal and the seal groove in at least one of the first scroll and the second scroll. The scroll fluid machine according to 1.   2. The radial width dimension of the first scroll and the second scroll changes in a stepwise shape from the center side toward the outer periphery side in at least one of the first scroll and the second scroll. The scroll fluid machine according to 1.   In at least one of the first scroll and the second scroll, the radial width dimension of the end portion on the center side of the seal groove is smaller than the width dimension of the end portion on the outer peripheral side of the tip seal. The scroll fluid machine according to claim 1, wherein:   4. The scroll type according to claim 3, wherein at least one of the first scroll and the second scroll, the tip seal on the center side and the tip seal on the outer peripheral side are separated. 5. Fluid machinery. A first scroll having an end plate and a wrap portion;
A second scroll having an end plate and a wrap portion and facing the first scroll;
A seal groove on the end plate side surface of the scroll facing the first scroll and the second scroll wrap portion;
A chip seal that seals between the first scroll and the second scroll in the seal groove;
In at least one of the first scroll and the second scroll, the tip seal includes a center tip seal including a center end portion and an outer periphery tip seal including an outer end portion, and the seal The groove is composed of a center side seal groove including an end portion on the center side and an outer periphery side seal groove including an end portion on the outer periphery side
The radial width dimension of the center side chip seal is smaller than the radial width dimension of the outer periphery side chip seal, and the radial width dimension of the central side seal groove is larger than the radial width dimension of the outer periphery side seal groove. A scroll type fluid machine.   The radial width dimension of the central seal groove is smaller than the radial width dimension of the outer peripheral tip seal in at least one of the first scroll and the second scroll. 6. A scroll fluid machine according to 6.   The scroll type fluid machine according to claim 6, wherein at least one of the first scroll and the second scroll, the center tip seal and the outer peripheral tip seal are separate. .

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