JP2009203986A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a lap or the like from being damaged when pressure of the attraction force generating space abnormally increases for pressing a non-turning scroll member to the turning scroll member side, and to improve assembling performance in a compressor, by easily incorporating a seal when forming an attraction force generating space, in a scroll compressor capable of moving the non-turning scroll member in the axial direction. <P>SOLUTION: Pressure of a non-turning attraction pressure area is set to a pressure or more of these peripheries. A sealing material of an elastic body is also arranged inside the non-turning attraction pressure area. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a scroll compressor in which a non-orbiting scroll member is movable in an axial direction.

  A conventional scroll compressor having a non-orbiting scroll member that is movable in the axial direction is provided with a non-orbiting attracting pressure region on the back surface of the non-orbiting scroll member as shown in Japanese Patent Application Laid-Open No. 8-232858. It was set to an intermediate pressure between the discharge pressure and the suction pressure. The inner peripheral side of the region is the discharge pressure and the outer peripheral side is the suction pressure, and a seal is provided at each boundary.

  The prior art reduces pressure in the working chamber by introducing pressure to the back surface of the fixed scroll and moving the fixed scroll to the counter-orbiting scroll side during overcompression. However, this structure has a problem that leakage loss and sliding loss due to delicate vertical movement of the orbiting scroll cannot be reduced.

  Moreover, in the said prior art, since the pressure of the non-rotating attraction | suction pressure area | region is an intermediate pressure, it was a pressure lower than the pressure (discharge pressure) of the space separated by the seal on the inner peripheral side. For this reason, when the seal is broken for some reason, there is a risk that the fluid of the discharge pressure flows into the non-swirl attracting pressure region and the pressure becomes higher than a normal level. At this time, the non-orbiting scroll member is urged by an excessive force to the orbiting scroll member that is the scroll support member. Therefore, the scroll wrap is destroyed or not reached, but due to abrupt wear of the tooth bottom. There is a problem that the reliability of the compressor is lowered because the wear powder may cause damage to sliding parts such as scroll wraps, bearings, and Oldham rings.

  In addition, since seals are provided at two locations on the inner and outer peripheral sides of the ring-shaped non-swirl attracting pressure region, it is necessary to incorporate even a single seal that requires careful attention. At the time of partition formation, two seals had to be incorporated almost simultaneously, and there was a problem that the assemblability was low.

  An object of the present invention is to provide a scroll compressor capable of reducing leakage loss and sliding loss.

  Another object of the present invention is to provide a scroll compressor that solves part workability.

  The above object has a scroll wrap on the end plate, a non-orbiting scroll member that can move in the axial direction without rotating, and a wrap that meshes with the wrap of the non-orbiting scroll member on the end plate, and performs a revolving motion by the drive shaft. In the scroll compressor comprising the orbiting scroll member, it is achieved by including means for introducing pressure for attracting both scroll members to the non-wrapping side of the non-orbiting scroll member and the anti-wrapping side of the orbiting scroll member. The

  In addition, the above object has a scroll wrap on the end plate, a non-orbiting scroll member that can move in the axial direction without rotating, and a wrap that meshes with the wrap of the non-orbiting scroll member on the end plate, and is rotated by the drive shaft. Means for introducing pressure for attracting both scroll members to the anti-wrap side of the non-orbiting scroll member and the anti-wrap side of the orbiting scroll member; And a valve provided in a hole communicating with the outside.

  Another object of the present invention is to have an orbiting scroll member that includes an end plate and a scroll wrap and rotates without rotating in a plane perpendicular to the axial direction, and an end plate and the scroll wrap, and is engaged with the orbiting scroll member. In a scroll compressor comprising a non-orbiting scroll member in which a compression chamber is formed and axial movement is allowed, the both scroll members are opposed to a pulling force in a direction to separate the scroll members in the axial direction. An attractive force adding means for applying an attractive force in the direction of attracting the scroll member in the axial direction to each of the scroll members, and a reaction force of an urging force that is the sum of the attractive force and the separating force. The scroll support member generated in the scroll member and the attractive force adding means provided on the non-orbiting scroll member of the attractive force adding means are connected to the end plate back of the non-orbiting scroll member. A non-orbiting end plate rear outer peripheral side which does not include the discharge port on the side, is achieved by providing a non-orbiting attracting regions to be more than the pressure of the non-orbiting attracting peripheral region of the peripheral region surrounding it.

  According to the present invention, it is possible to provide a scroll compressor capable of reducing leakage loss and sliding loss.

  Moreover, there is an effect that it is possible to provide a scroll compressor that solves part workability.

The longitudinal cross-sectional view of a 1st Example. The other longitudinal cross-sectional view of a 1st Example. The cross-sectional enlarged view of the compression chamber vicinity of a 1st Example. The cross-sectional enlarged view near the ring groove of the first embodiment. Sectional drawing of the ring seal of a 1st Example. The longitudinal cross-sectional view of the backflow suppression valve body of a 1st Example. The top view of the backflow suppression valve body of a 1st Example. The top view of the retainer of a 1st Example. The top view at the time of the subassembly which attached the backflow suppression valve and the ring seal to the non-orbiting scroll member of the first embodiment. The top view of the discharge cover of a 1st Example. The expanded sectional view of the back pressure valve of the first example. The expanded sectional view of the ring seal of the 2nd example. The expanded sectional view of the ring seal of the 3rd example.

  A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a compressor, and FIG. 2 is the same longitudinal sectional view, but a different cross section from FIG. In FIG. 2, only parts that did not appear in FIG. 1 are marked. 3 is an enlarged cross-sectional view of the vicinity of the compression chamber, FIG. 4 is an enlarged cross-sectional view of the vicinity of the ring groove forming the non-rotating attraction pressure region, FIG. 5 is a cross-sectional view of the ring seal that is an elastic seal, and FIG. FIG. 7 is a plan view of the backflow suppression valve body, FIG. 8 is a plan view of the retainer, and FIG. 9 is a top view at the time of subassembly in which the backflow suppression valve and the ring seal are mounted on the non-orbiting scroll member. FIG. 10 is a top view of the discharge cover, and FIG. 11 is an enlarged cross-sectional view of the back pressure valve. In this example, the compressor has a diameter of about 5 mm to 1000 mm at the micromachine level, and is a low-pressure chamber system in which the inside of the compressor case has a suction pressure.

First, the structure will be described.
The orbiting scroll member 3 is provided with a scroll wrap 3b and Oldham grooves 3g and 3h (see FIG. 2) on the upper surface of the end plate 3a, and a thrust surface 3d and an orbiting shaft 3e on the lower surface of the end plate. A swirl oil groove 3c is provided on the thrust surface 3d.

  The non-orbiting scroll member 2 is provided with a scroll wrap 2b and rotation stoppers 2g and 2h (2h is arranged integrally with a portion not serving as a seal portion on the outer peripheral side of the scroll wrap 2b) on the lower surface of the end plate 2a, A non-turning reference surface 2u (see FIG. 2) that is the same surface as the scroll wrap tooth bottom surface is provided. The rotation stoppers 2g and 2h are fitted in a groove provided in the non-orbiting holder 6 to prevent the non-orbiting scroll 2 from rotating. The rotation stoppers 2g and 2h may be any one of these.

  Then, the bypass hole 2e and the discharge hole 2d are opened. In addition, a ring groove 2j that communicates with the inner space 2f of the end plate in which the discharge hole 2d is opened by one or a plurality of equalizing channels 2i is provided around the upper surface of the end plate 2a. Since the discharge pressure can be introduced into the non-swirl attracting pressure region 29 only by the pressure equalizing flow path 2i, there is an effect that workability is improved and high mass productivity can be realized. In this embodiment, there is an oblique single hole, and there is a specific effect that the number of processing steps is further reduced and higher mass productivity can be realized. Further, a horizontal hole may be formed from the outer periphery of the non-orbiting scroll member 2 to block the outer flange through portion. In this case, drilling is easy. In the case where the pressure equalizing flow path 2i is one, the number of processing steps can be reduced and the mass productivity can be improved, and the flow of gas through the non-swirl attracting pressure region 29 does not occur. There is a specific effect that it is suppressed and the performance is improved. On the other hand, when there are a plurality of pressure equalizing channels 2i, the introduction of pressure into the non-swivel attracting pressure region 29 is instantaneously performed, and there is an effect that the activation becomes easy.

  A backflow suppression valve 24 (see FIGS. 6 to 9) including a backflow suppression valve plate 24a and a retainer 24b is installed above the bypass hole 2e and the discharge hole 2d of the non-orbiting scroll member 2. This plays a role of a bypass valve for suppressing overcompression and avoiding liquid compression, a check valve for preventing reverse rotation of the orbiting scroll generated when the compressor is stopped, and a discharge valve for suppressing undercompression. The retainer 24b functions as a valve stopper when these valves are opened, and has an effect of suppressing flapping of the valves.

  Further, a ring seal 22 is inserted into the ring groove 2j of the non-orbiting scroll member 2 as an elastic seal having a U-shaped cross section made of an elastic material such as plastic, spring material or rubber (FIG. 4). 5). Here, the height of the seal is made smaller than the depth of the ring groove 2j, and the inner peripheral wall is made shorter than the outer peripheral wall. Thereby, even if the ring seal 22 is lowered to the bottom of the ring groove 2j, the inner peripheral wall can be prevented from blocking the pressure equalizing flow path 2i. Further, as shown in FIG. 5, a seal spring 22 a having a semicircular cross section is inserted into the ring seal 22. When the ring seal 22 is inserted into the ring groove 22j, the seal spring 22a functions to press the inner peripheral wall and the outer peripheral wall of the ring seal 22 against the inner wall of the ring groove 2j. Due to the function of the seal spring 22a, the adhesion between the ring seal 22 and the ring groove 2j is improved, and there is an effect that pressure leakage is reduced.

  Further, the pressure equalizing flow path 2i is formed with a horizontal hole in the non-rotating end plate 2a, and a substantially vertical hole is formed from the bottom surface of the ring groove 2j and the bottom surface of the mirror slope inner space 2f so as to communicate with the hole. If the outer periphery of the horizontal hole is closed, the pressure equalizing flow path 2i is not blocked even if the ring seal is lowered, and the reliability is improved.

  As described above, since the seal portion of the non-orbiting attracting pressure region 29 that requires careful attention to the assembly can be performed at the time of sub-assembly of the non-orbiting scroll member 2, a seal check after assembly or a problem occurs. This makes it easy to reassemble the assembly and greatly improves the assemblability.

  The Oldham ring 5 is provided with non-rotating protrusions 5a and 5b on one surface, and as shown in FIG. 2, rotating protrusions 5c and 5d are provided on the other surface. The cylindrical non-orbiting holder 6 has a terrace portion 6a that protrudes into a central hole and supports the non-orbiting scroll member 2, and the upper surface thereof becomes a non-orbiting support surface 6b. The inner peripheral surface of the upper part becomes a guide surface 6c that serves as a guide when the non-orbiting scroll member 2 moves up and down. Furthermore, two radiating grooves 6d and 6e are provided on the terrace portion 6a so as to face each other by 180 degrees about the central axis of the guide surface. The upper portions of the grooves insert the rotation stoppers 2g and 2h of the non-orbiting scroll member 2, and the lower portion serves as an Oldham groove in which the non-orbiting protrusions 2a and 2b of the Oldham ring 5 slide.

  The radial grooves 6d and 6e serve to prevent the rotation of the Oldham ring 5 by inserting the non-turning protrusions 5a and 5b of the Oldham ring 5, and the rotation stoppers 2g and 2h of the non-turning scroll member 2 When inserted, it also serves to prevent the rotation of the non-orbiting scroll member 2. The non-orbiting scroll member 2 and the Oldham ring 5 try to rotate in the same direction by the orbiting motion of the orbiting scroll member 3. In order to prevent these rotations in different grooves, the positions for digging each groove must be performed with high accuracy. However, in the present embodiment, since the grooves for stopping both rotations are also used, positioning can be performed without having to consider the accuracy of the grooves. That is, since both receive the force rotated in the same direction, the pressure receiving surface on the groove side is the same surface for both the non-orbiting scroll member 2 and the Oldham ring 5. Therefore, the surface that does not become the pressure receiving surface of the groove is not required to have high machining accuracy.

  The frame 4 is provided with a holder mounting surface 4b for mounting the non-orbiting holder 6 on the outer periphery of the upper surface, and a thrust bearing 4a serving as a support surface for the orbiting scroll member 3 inside the same surface. The thrust bearing 4a is provided with a plurality of frame oil grooves 4c for the purpose of supplying oil to the thrust bearing portion and supplying oil to the suction chamber. Further, one or a plurality of suction ports 4e that pass through the frame 4 in the axial direction and allow suction gas to flow are provided. This may be a notch on the outer periphery of the frame, or may be provided on the non-rotating holder 6. A central bearing 4d that rotatably supports the shaft is provided at the center. An oil discharge passage is provided between the main bearing 4d and the thrust bearing 4a to the outer peripheral surface of the frame 4, and a back pressure valve 10 (FIG. 11) is formed in the middle. The back pressure valve 10 is formed as follows. First, the back pressure valve body 10a whose outer periphery is polished is inserted into the back pressure valve cylinder 4g whose inner diameter is polished from the side surface of the frame 4. Then, the valve spring 10c is inserted, and the valve cap 10f is fixed to the inlet of the back pressure valve cylinder 4g so that it becomes a compression spring.

  Returning to FIG. 1, the shaft 8 is provided with a shaft oil supply hole 8a, a main bearing oil supply hole 8b, and a sub-bearing oil supply hole 8c. In addition, a main shaft portion 8h having an enlarged diameter is provided at an upper portion thereof, and a swing bearing 8f is provided there. An oil supply spiral groove 8i is provided on the outer peripheral surface of the main shaft portion from the outlet of the main bearing oil supply hole 8b, and an oil supply groove 8j is provided on the swing bearing 8f.

  The rotor 15 incorporates an unmagnetized permanent magnet (not shown), and is provided with rotor balances 15a and 15b at both ends.

  The stator 16 is provided with a stator groove 16a (FIG. 2) for allowing oil to flow down to the bottom of the case on the outer periphery, and a coil passes inside, and a coil end portion 16b is provided above and below. Incidentally, the stator 16 may be cooled by forming a coil through hole on the outer peripheral side of the hole through which the coil passes, and passing a gas flow or oil.

  The sub-bearing oil supply section 9 is composed of a floating bearing bush 9a having a cylindrical inner periphery and a spherical outer periphery, a sub-bearing oil supply cylinder 9b, and a pump cover 9c with an oil supply pipe 9d. The countershaft oil supply cylinder 9b has a spherical bearing portion 9g on the upper inner periphery, and the floating bearing bush 9a is incorporated therein. Further, a shaft thrust surface 9e which is an axial support portion of the shaft 8 is disposed at the upper center. In addition, an eccentric circular excavation 9f into which the inner rotor 26a and the outer rotor 26b of the trochoid oil pump 26 enter is provided at the lower part thereof. This is not limited to the trochoid oil pump, but may be another type oil pump.

  The case includes three parts, an upper case 19, a lower case 20, and a cylindrical case 21, to which a hermetic terminal 13 and a discharge pipe outlet 19a are welded or brazed. A sub-bearing oil supply support plate 18 having a hole through which oil passes in the periphery is fixed.

  Other main components include a non-rotating presser 7 for holding the ring seal 22, a mounting member 11 for fixing the frame 4 to the cylindrical case 21, a magnet 12 for removing iron powder in oil, and electric power for a motor 17. There is a hermetic terminal 13 and a suction pipe 14 to be fed to.

These components are assembled as follows.
First, the shaft 8 into which the rotor 15 is press-fitted is inserted into the main bearing 4d of the frame 4, and the orbiting scroll member 3 is placed thereon. Further, the Oldham ring 5 is placed on the orbiting protrusions 5c and 5d inserted into the Oldham grooves 3g and 3h, and the non-orbiting scroll member 2 is placed on the non-orbiting holder 6 above the radiation grooves 6d and 6e. The one mounted so that the rotation stoppers 2g and 2h are inserted is covered from above. At this time, the non-rotating protrusions 5a and 5b are inserted below the radiation grooves 6d and 6e, and the non-turning reference surface 2u is brought into contact with the non-turning support surface 6b. Then, the non-turning holder 6 is fixed to the frame 4 with screws at a position where the rotational torque is minimum while rotating the shaft 8. Then, the non-orbiting press surface 7 a of the non-orbiting presser 7 is fixed to the upper surface of the non-orbiting holder 6 with screws so as to cover the outer periphery of the non-orbiting scroll member 2 and the ring seal 22. As a result, a ring-shaped non-rotating attracting pressure region 29 is defined by the non-rotating presser 7 and the ring groove 2j. At the same time, the ring seal 22 inserted into the ring groove at the time of sub-assembly of the non-orbiting scroll member 2 is viewed from the non-orbiting attracting pressure region 29 and the upper edge of the ring groove 2j and the non-orbiting pressing surface. It arrange | positions so that the non-rotation attraction | suction pressure area | region boundary which is a boundary part with 7a may be covered. At this time, the distance between the upper surface of the non-orbiting scroll member 2 and the non-orbiting pressing surface 7a is set to about 20 to 100 μm, and the maximum separation distance in the axial direction between the orbiting scroll member 3 and the non-orbiting scroll member 2 is set. Stipulate. Then, as shown in FIGS. 1 and 10, a discharge cover 2c with a discharge pipe 25 is closely fixed to the center of the non-rotating end plate 2a facing the discharge port 2d and the bypass hole 2e, and the end plate inner space 2f is fixed. Is provided. At this time, both contact surfaces are polished or sealed with an O-ring or packing material interposed therebetween. The discharge pipe 25 is annealed. This is because when the discharge pipe 25 is fixed to the upper case 19, the displacement of the mounting position of the upper case 19 is absorbed by the discharge pipe 25 to prevent the non-orbiting scroll member 2 from being displaced. As described above, the compression chamber 33 is formed between the scroll members, and the orbiting back space 34 is formed between the thrust surface 3d and the orbiting shaft 3e on the back surface of the orbiting scroll member 3. Further, the mounting member 11 is screwed or caulked to the outer periphery of the back surface of the frame 4.

  Next, the assembly portion is inserted into a cylindrical case 21 in which the stator 16 is shrink-fitted or press-fitted in advance and the auxiliary bearing oil supply support plate 18 is welded or press-fitted. At this time, the motor wire 16c of the stator 16 is put out through the groove on the side surface of the assembly portion. Then, tack welding is performed on the side surface of the mounting member 11. Compared with the case where tack welding is performed with the frame 4 or the non-rotating holder 6, such deformation can be avoided. A motor 17 is formed by the rotor 15 and the stator 16, and a motor chamber 30 is formed between the auxiliary bearing oil supply support plate 18 and the frame 4.

  Next, the inner periphery of the floating bearing member 9a of the non-slewing oil supply member 9 is inserted and attached to the shaft 8 protruding from the central hole of the auxiliary bearing oil supply support plate 18. Then, the outer rotor 26b is inserted into the auxiliary bearing oil supply cylinder 9b, and the inner rotor 26a is press-fitted into the end portion of the shaft 8. In this state, the shaft 8 is rotated to detect the rotational torque, and the position of the auxiliary bearing oil supply cylinder 9b is adjusted, and the outer periphery of the auxiliary bearing oil supply cylinder 9b is positioned at the position where the rotational torque is minimized. Spot welding is performed on the oil supply support plate 18. And the said oil supply cover 9c which attached the said oil supply pipe 9d is fixed.

  Finally, the lower case 20 to which the magnet 12 is fixed is welded to the cylindrical case 21 to form an oil storage chamber 31. The upper case 19 is mounted on the inner terminal of the discharge hermetic terminal 13 with the motor wire 16c, and the vertical portion 25a of the discharge pipe 25 is passed through the discharge pipe outlet 19a. The upper part 21 is attached and welded to form a non-revolving back chamber 32. In this state, a current is passed through the stator 16 to magnetize the permanent magnet inside the rotor 15 to form the motor 17. Then add the oil.

Next, the operation will be described.
First, the flow of compressed gas will be described. The shaft 17 is rotated by rotating the motor 17, and the orbiting scroll member 3 is revolving while preventing rotation by the Oldham ring 5. Gas filled in the case through the suction pipe 14 flows into the suction chamber 35 through the suction port 4e, is closed and compressed in the compression chamber 33, and is discharged from the discharge hole 2d to the end plate space 2f. Finally, it goes out of the compressor through the discharge pipe 25. Under the overcompression condition, in parallel with this, the gas is discharged into the end plate space 2 f through the bypass hole 2 e and the bypass valve portion of the backflow prevention valve 24. Thereby, the space 2f in the end plate becomes a discharge pressure. Furthermore, the upper part is the non-swirling back chamber 32 of the suction pressure, and forms a non-swirling back center region where the suction pressure is applied. Since the suction pressure is applied to the center region of the non-revolving back surface, the deflection of the non-revolving end plate 2a is reduced, and the tooth tip bottom gap can be reduced, so that the energy efficiency is improved. By the pressure equalizing flow path 2i, the inside of the non-rotating attraction pressure region 29 defined by the ring groove 2j and the ring seal 22 can be easily set as a discharge pressure. And all the circumference | surroundings of the said non-rotation attraction | suction pressure area | region 29 become the space of a suction pressure. That is, since the inner peripheral side of the ring seal 22 communicates with the non-swirl back chamber 32 and the outer periphery communicates with the suction chamber 35 or the non-swirl back chamber 32, suction pressure is obtained. For this reason, since the non-swirl attracting pressure region 29 is the highest pressure inside the compressor, the pressure inside the non-swirl attracting pressure region 29 does not increase even if the seal is broken, The attraction force, which is the force that acts in the direction in which the scroll member 2 and the orbiting scroll member 3 are brought into contact (attached), does not become excessive.

  In other words, since the non-orbiting scroll member is provided with a non-orbiting attraction area that is equal to or higher than the pressure of the non-orbiting attraction peripheral area, which is a peripheral area surrounding the non-orbiting end panel on the outer peripheral side of the non-orbiting end panel that does not include the discharge port. Since the pressure in at least one non-swirl attracting region is equal to or higher than the pressure in all surrounding non-swirl attracting regions, even if the seal there is broken, the ambient pressure generates a pulling force. In the prior art higher than the pressure, if the seal is broken, the attracting force increases, whereas the pressure in the non-rotating attracting region does not increase. As a result, there is an effect that a reduction in the reliability of the compressor due to an increase in the pulling force of the non-orbiting scroll, which is a problem of the prior art, is suppressed.

  Further, since the discharge pressure is the highest pressure in the compressor, the pressure in all the non-swirl attracting regions is equal to or higher than the pressure in each non-swirl peripheral region. Therefore, even during transient operation up to steady operation, the pressure in all non-swirl attracting areas can be maintained at or above the pressure in the non-swirl peripheral area. This can be avoided more reliably. As a result, there is an effect that the reliability of the compressor is further improved. Further, since the non-swirl attracting force is generated by the discharge pressure that is the highest pressure in the compressor, the volume of the non-swivel attracting region is almost minimized. Accordingly, since the length of the non-swirl attracting pressure region boundary is generally reduced, the risk of leakage from the non-swirl attracting region can be reduced. As a result, the risk of lowering the attractive force can be reduced, so that the original performance can be reliably realized.

  As a result, it is possible to avoid damage to the terrace portion 6a of the non-revolving holder 6 where the urging force is applied. Even if it does not lead to breakage, it is possible to suppress the tooth bottom contact wear and the risk of breakage of the scroll wrap due to the deflection. Further, since the ring seal 22 tries to open left and right due to the pressure difference, the side surface is pressed against the inner peripheral surface and the outer peripheral surface of the ring groove. As a result, the ring seal covers the boundary between the non-swirl attracting pressure region, which is the boundary between the upper edge of the ring groove 2j and the non-swirl holding surface 7a, as viewed from within the non-swirl attracting pressure region 29. Therefore, two seals can be performed on the inner peripheral side of the non-swirl attracting pressure region 29 and the non-swivel attracting pressure peripheral region on the outer peripheral side. In the past, since seals were provided at two locations, assembling of seals requiring the utmost care was required, and when two seals were incorporated at the same time when the non-rotating attraction pressure zone was formed. Compared with this, there is an effect that the assemblability can be greatly improved.

  That is, since the pressure in the non-swirl attraction pressure region is higher than the pressure in the non-swing attraction pressure peripheral region, the elastic seal is pressed against the non-swing attraction pressure region boundary side, and the non-swing attraction by its elasticity. It deforms so as to close the entire boundary of the pressure area. As a result, the seal in the non-swirl attraction pressure region and the non-swirl attraction pressure peripheral region is further ensured, and there is an effect of improving the reliability and performance of the compressor. Furthermore, since the non-swivel attracting pressure region can be formed with a single seal, there is an effect that the assemblability can be improved.

  Further, since the non-orbiting scroll member in which the elastic body seal is inserted in the ring groove can be prepared in advance, it is not necessary to form a seal portion by the elastic body seal when the compressor is assembled. Therefore, it is possible to form the seal portion by the elastic seal that requires careful assembly at the sub-assembly stage of the non-orbiting scroll member. As a result, there is an effect that the assemblability is further improved.

  Since the non-turning support surface 6b of the non-turning holder 6 is arranged below, there is an effect that the deformation of the non-turning end plate 2a is suppressed and the energy efficiency becomes very high. The ring seal 22 is lifted upward by the same force as the pulling force, but is stopped by the non-rotating presser foot 7. Further, since the non-revolving back chamber 32 becomes the suction pressure, the pressure inside the case of the compressor becomes the suction pressure throughout. As a result, the hermetic terminal 13 may be provided in any part of the case, which has a specific effect that the manufacturability is improved.

  At the outlet of the discharge hole 2d, a central valve body 24c serving as a check valve and a discharge valve among the check valve 24 is provided (see FIGS. 6 to 9). This is supported by the three valve legs 24d, and the neutral position is a position that is away from the conical surface above the discharge hole 2d and substantially contacts the retainer 24b. As a result, during over-compression operation or proper pressure ratio operation, gas can be discharged without pushing up the central valve body 24c, so that the discharge channel resistance is very small and the performance is improved. Further, when the reverse flow from the Kazaka slope space 2f to the discharge hole 2d due to insufficient compression, the central valve element 24c closes the discharge hole 2d by a fluid force, so that the swell of the acupressure diagram due to the reverse flow is eliminated and the performance is improved. There is a unique effect. Further, since the central valve body 24c close to the conical discharge hole 2d is used, the re-expansion loss can be suppressed and the performance can be improved. In this way, the discharge valve appears only when the discharge valve is necessary, and there is a specific effect that extremely high efficiency can be realized at the total pressure ratio of operation. In addition, when the compressor stops, the central valve body 24c closes the discharge hole 2d by a fluid force at the time of back flow from the Kagamizaka inner space 2f to the discharge hole 2d, so that it is possible to suppress reverse rotation of the orbiting scroll member 3. is there.

  As described above, the single backflow suppression valve 24 serves as a bypass valve, a discharge valve, and a check valve. Therefore, the number of components can be suppressed and mass productivity can be improved. Further, the structure of this valve portion can be produced by bending a single plate and outsert-molding the central valve body 24c made of plastic, and thus has a specific effect of improving mass productivity. .

  Further, a conformable film (not shown) is provided on the front surface side of the scroll wrap 3b and the orbiting end plate 3a of the orbiting scroll member 3. As a result, as described above, it is possible to avoid an increase in the gap due to an error in the component size that determines the tooth tip bottom gap, so that the energy efficiency can be further improved.

  Next, the flow of oil will be described. The oil in the oil storage chamber 31 is sucked up from the oil supply pipe 9d by the trochoid oil supply pump 26 provided at the lower end of the shaft 8, and enters the shaft oil supply hole 8a. Here, a slight amount of oil passes through the gap between the upper surface of the inner rotor 26a and the circular digging 9f and supplies the shaft thrust surface 9e. The oil feeds the spherical bearing portion 9g on the outer periphery of the floating bearing bush 9a and exits to the lower portion of the motor chamber 30. Thereafter, the auxiliary bearing oil supply support plate 18 returns to the oil storage chamber 31 from the oil hole 18a in the outer peripheral portion. Part of the oil that has entered the shaft oil supply hole 8a first enters the auxiliary bearing oil supply hole 8c, and supplies oil to the cylindrical bearing of the floating bearing bush 9a. Thereafter, the oil passes through the spherical bearing portion 9g or directly enters the motor chamber 30 and returns to the oil storage chamber 31 through the oil hole 18a. The oil that has not entered the auxiliary bearing oil supply hole 8c further moves up the shaft oil supply hole 8a, enters the main bearing oil supply hole 8b, and supplies the main bearing 4d and the swing bearing 8f. The main shaft portion 8h is provided with the oil supply spiral groove 8i, and the oil supply amount to the main bearing is determined by the screw pump action. The other amount flows to the slewing bearing 8f. There is provided an oil supply groove 8j, which serves as an oil sump for supplying oil to the entire slewing bearing. The oil that has been supplied with oil flows into the revolving back space 34. Here, since the back pressure valve 10 is provided, the pressure in the revolving back space 34 is higher than the suction pressure by a value corresponding to the amount of compression of the valve spring 10c. The operation will be described below.

  In FIG. 11, when the back pressure is low, the back pressure valve body 10a is pressed against the bottom surface of the back pressure valve cylinder 4g, and the oil inflow passage 4h is blocked by the side surface of the back pressure valve body. As a result, oil is not discharged from the swivel back space 34, and the pressure there rises. Since this pressure (hereinafter referred to as back pressure) is guided to the back pressure detection space 10d by the oil detection path 4i, the force for pushing the back pressure valve body 10a toward the valve cap 10f increases, and the back pressure valve body 10a is Move to the cap 10f side. Then, when the back pressure increases until the movement of the oil passage groove 10e reaches the place where the oil passage groove 10e is applied to the oil inflow passage 4h, the oil in the oil passage 10g and the valve cap 10f at the bottom of the oil passage groove 10e. An oil passage from the turning back space 34 to the side surface of the frame 4 is formed by the discharge path 10i, and the oil flows out of the turning back space 34, so that the back pressure stops rising. In this way, the back pressure is controlled to a pressure that is a certain value higher than the suction pressure, which is the pressure on the side surface of the frame 4. When pressure is guided to the back pressure detection space 10d, the back pressure valve body 10a moves to the right side of the drawing against the spring force. At this time, if the pressure of the lubricating oil guided to the turning back space suddenly increases for some reason, the oil passage groove 10e goes to the right after passing through the oil inflow passage 4h, and the pressure in the turning back pressure space 34 does not naturally drop. As long as the pressure in the turning back pressure space 34 remains high. Therefore, in the present embodiment, the anti-back pressure detection space 10d side of the back pressure valve body 10a abuts on the top of the valve cap 10f, so that even if the pressure in the turning back pressure space 34 suddenly rises, The inflow channel 4h is stopped at a position facing it. As a result, the back pressure is reliably controlled to a pressure higher than the suction pressure that is the pressure on the side surface of the frame 4 by a certain value.

  As a result, the pressure in the orbiting back space 34 becomes higher than the suction pressure, so that an attractive force of the orbiting scroll member 3 is generated. However, this force is set to be smaller than the turning pulling force. As a result, the orbiting scroll member 3 has a rear surface of the end plate 3a serving as a thrust surface, and the urging force applied thereto, that is, the thrust bearing load can be reduced. For this reason, the sliding loss in the location can be reduced and there exists a characteristic effect that energy efficiency improves.

  Further, in FIG. 3, an oil throttle passage connecting the revolving back space 34 and the suction chamber 35 is provided by the frame oil groove 4c of the thrust bearing 4a and the revolving oil groove 3c of the thrust surface 3d. An oil path is also formed which flows into the suction chamber 35 while the thrust surface is refueled by a pressure difference caused by the back pressure valve. Thereby, in addition to the effect of improving the reliability of the thrust bearing and the performance improvement by reducing the friction coefficient, there is also the effect of improving the performance by improving the sealing performance in the compression chamber 33.

  The oil discharged to the side surface of the frame then flows downward along the inner wall of the cylindrical case 21, passes through the mounting outer circumferential groove 11a of the mounting member 11 and the stator outer circumferential groove 16a, and finally the oil storage chamber 31. Flow into. Further, since the intermediate pressure in the revolving back space 34 does not need to be supplied from the outside, there is a specific effect that the usability is improved.

  Here, an example in which the suction pressure in the case is used and the pressure in the non-swing attracting pressure region is used as the discharge pressure is shown, but not limited to this, the pressure in the non-swirl attracting pressure region is higher than the case internal pressure. If it is. For example, the inside of the case may be the suction pressure, and the pressure in the non-swing attractive pressure region may be an intermediate pressure. Further, the inside of the case may be an intermediate pressure, and the pressure in the non-swing attractive pressure region may be a discharge pressure. Of course, a plurality of non-swirl attracting pressure regions may be provided. Of course, the present invention can also be applied to a scroll compressor having a structure in which the non-orbiting scroll member is pressed against the orbiting scroll member.

  Now, the operation of the scroll compressor described above will be described. The conventional scroll compressor applies a back pressure to the half lap side of the orbiting scroll, and the orbital scroll movable distance is more than 50 μm, and the behavior when the orbiting scroll is actually operated is examined. In some cases, the shaft may swing in the axial direction due to pressure balance between the left and right working chambers and other manufacturing errors. When such movement moves in the direction in which the orbiting scroll is pulled away from the fixed scroll (non-orbiting scroll), the compressed fluid leaks from the high-pressure working chamber to the low-pressure working chamber, causing a loss. When moving in the direction pressed against the scroll, there is a problem that the tooth tip of the scroll wrap and the end plate come into contact with each other and the sliding resistance increases.

  In the present embodiment, an intermediate pressure larger than the suction pressure and smaller than the discharge pressure is applied to the back surface of the orbiting scroll member 3, and a discharge pressure larger than this intermediate pressure is applied to the back surface of the fixed scroll member 3, The movement of the orbiting scroll 3 in the axial direction is restricted by the non-orbiting holder 6 and the movable distance is suppressed within a range of 50 μm. Therefore, even if the orbiting scroll member 3 swings in the axial direction, that is, both scrolls. When the orbiting scroll moves in the direction in which the member is released, since the discharge pressure higher than the intermediate pressure is applied to the back surface of the non-orbiting scroll member 2, it is possible to reduce leakage loss by following the movement, Further, when the orbiting scroll member 3 moves in a direction in contact with the non-orbiting scroll member 2, the non-orbiting scroll member 2 is moved in the axial direction semi-non-orbiting scroll. It is possible to reduce the loss due to galling because moving the seal member side. Here, during overcompression, the orbiting scroll member 3 behaves away from the non-orbiting scroll member 2, but the non-orbiting scroll member 2 moves so as to follow this. At this time, a working fluid (refrigerant) moves from the overcompressed compression chamber to the compression chamber having a low pressure due to a slight gap between the scroll wrap and the end plate. However, the compression chamber also becomes overcompressed at the next moment, and the overcompressed state is not improved forever. Therefore, in the present embodiment, the backflow suppression valve plate 24a is provided, and the pressure is released by letting the working fluid escape from the working chamber which is a sealed space.

  That is, the non-orbiting scroll member 2 is operated in a state where it floats from the non-orbiting presser 7, and the orbiting scroll member 3 is operated in a state where it floats from the thrust bearing 4a. For this reason, since the non-orbiting scroll member 2 operates so as to follow the swinging motion of the non-orbiting scroll member 2 in the axial direction, a reduction in loss can be expected as described above.

  Actually, the pressure applied to the back surface of the non-orbiting scroll member 2 (non-orbiting attracting pressure region 29) is a discharge pressure, and the pressure applied to the back surface of the orbiting scroll member 3 (orbiting back space 34) is a so-called intermediate pressure. Therefore, only a few μm order floats between the orbiting scroll member 3 half-wrap side surface and the thrust surface 3d. Lubricating oil has entered this floating space. For this reason, of the swinging motion of the orbiting scroll member 3 in the axial direction, the motion in the direction away from the non-orbiting scroll 2 due to the pressure increase (overcompression) in the compression chamber is suppressed by the thrust surface 3d which is a thrust bearing. . At this time, the backflow suppression valve plate 24a is opened to release the overcompressed state.

  On the other hand, when the orbiting scroll member 3 moves in a direction approaching the non-orbiting scroll member 2 for some reason, the non-orbiting scroll member 2 moves in the anti-orbiting scroll member 3 direction, and the galling is alleviated.

  In the case of so-called liquid compression for sucking liquid refrigerant, since a considerable force is applied to both scroll members, both scroll members move in directions away from each other, so that the scroll wrap breakage due to liquid compression is effectively suppressed. be able to.

  In the present embodiment, the low-pressure chamber method in which the inside of the sealed container containing the compression mechanism unit and the electric mechanism unit is used as the suction pressure has been described. However, regarding the method of floating both scroll members, the inside of the sealed container is discharged. The same effect is also obtained in a high-pressure chamber system that uses a pressure or an intermediate pressure.

  Next, a second embodiment of the ring seal 22 will be described using an enlarged cross-sectional view of the ring seal 22 in FIG. Since it is the same as that of the first embodiment except that a seal spring 22a is mounted on the inner surface of the plastic U-shaped ring seal 22, the description other than that portion is omitted. As a result, even when there is no pressure difference between the inside and outside of the ring seal at the time of startup, the sealing performance can be secured by the spring force, so that the discharge gas does not flow into the swivel back space 34 and the suction chamber 35, and startup can be performed smoothly. There is an effect.

  Next, a third embodiment of the ring seal 22 will be described using an enlarged sectional view of the ring seal 22 of FIG. Since it is the same as that of the second embodiment except that the inner surface of the plastic U-shaped ring seal 22 is fitted with a pressure-bonding seal spring 22b that is pressure-bonded to the bottom of the ring groove 2j, the description other than that portion is omitted. Thereby, even when the pressure difference between the inside and outside of the ring seal immediately after activation is small, the non-swivel attracting force can be applied by the spring force, so that the activation can be performed more smoothly.

  2 ... non-orbiting scroll member, 2j ... ring groove, 3 ... orbiting scroll member, 4 ... frame, 5 ... Oldham ring, 6 ... non-orbiting holder, 8 ... shaft, 10 ... back pressure valve, 22 ... ring seal, 24 ... backflow control valve, 26 ... oil supply pump, 29 ... non-swirl attracting pressure region, 33 ... compression chamber, 34 ... revolving back space.

Claims (7)

  A non-orbiting scroll member that has a scroll wrap on the end plate and that can move in the axial direction without rotating, and a orbiting scroll member that has a lap that meshes with the wrap of the non-orbiting scroll member on the end plate and that makes a revolving motion by the drive shaft A scroll compressor comprising: means for introducing pressure for attracting both scroll members to the anti-wrap side of the non-orbiting scroll member and the anti-wrap side of the orbiting scroll member.   A non-orbiting scroll member that has a scroll wrap on the end plate and that can move in the axial direction without rotating, and a orbiting scroll member that has a lap that meshes with the wrap of the non-orbiting scroll member on the end plate and that makes a revolving motion by the drive shaft A scroll compressor comprising: means for introducing pressure for attracting both scroll members to the non-wrapping side of the non-orbiting scroll member and the anti-wrapping side of the orbiting scroll member; A scroll compressor including a valve provided in a communicating hole.   A revolving scroll member having an end plate and a scroll wrap and revolving without rotating in a plane perpendicular to the axial direction, a end plate and a scroll wrap, and a compression chamber is formed by meshing with the orbiting scroll member, In a scroll compressor comprising a non-orbiting scroll member that is allowed to move in the axial direction, the scroll members are pulled in the axial direction against a pulling force in a direction to separate the scroll members in the axial direction. An attractive force adding means for applying an attractive attractive force to each of the scroll members, and a scroll support member for generating a reaction force of an urging force, which is the sum of the attractive force and the separating force, in each of the scroll members. And the attractive force adding means provided on the non-orbiting scroll member of the attractive force adding means does not include a discharge port on the back surface side of the non-orbiting scroll member. The orbiting end plate rear outer peripheral side, the scroll compressor having a orbiting attracting region equal to or higher than the pressure of the non-orbiting attracting peripheral region of the peripheral region surrounding it.   4. The scroll compressor according to claim 3, wherein the pressure in the non-swirl attracting pressure region is a discharge pressure.   4. The scroll compressor according to claim 3, further comprising a pressure equalizing channel that communicates the non-orbiting attracting pressure region and the non-orbiting end plate back center side including the discharge port on the end plate rear side of the non-orbiting scroll member.   6. The non-swirl attracting pressure region according to claim 3, 4 or 5, wherein the non-swirl attracting pressure region is a boundary between the non-swirl attracting pressure region and the non-swirl attracting pressure peripheral region. The scroll compressor which arrange | positioned the elastic body seal which covers a boundary and does not cover the pressure inlet which introduce | transduces a pressure into the said non-rotation attraction | suction pressure area | region.   In claim 6, the non-swirl attracting pressure region is partitioned from a ring groove formed around the discharge port on the back side of the non-swirl end plate, and a seal support disposed so as to cover the ring groove, A scroll compressor having a shape and an arrangement in which an elastic seal is in contact with at least three surfaces of an inner circumferential surface and an outer circumferential surface of the ring groove in the non-rotating attraction pressure region and the seal support surface.

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