JP2001289181A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the assembling workability of a scroll compressor having a non-rotary scroll member movable in axial direction by preventing a lap from being damaged due to an abnormal rise of pressure in an attracting force generating space for pressing the non-swing scroll member against a swing scroll member and by facilitating the installation of a seal when the attracting force generating space is formed. SOLUTION: A pressure in a non-rotary attracting pressure area is set higher than that around the area. Also, an elastic seal member is disposed in the non- rotary attracting pressure area.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art A conventional scroll compressor having a non-orbiting scroll member movable in the axial direction is disclosed in Japanese Patent Application Laid-Open No. H8-2328.
As disclosed in Japanese Patent Application Publication No. 58-58, a non-orbiting pulling pressure region is provided on the back surface of the non-orbiting scroll member, and the inside thereof is set to a pressure intermediate 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 of these boundaries.

[0003]

In the prior art, the pressure in the working chamber is reduced by introducing pressure to the back of the fixed scroll to move the fixed scroll to the anti-orbiting scroll side during overcompression. . However, this structure has a problem that it is impossible to reduce the leakage loss and the sliding loss due to the subtle vertical movement of the orbiting scroll.

In the prior art, since the pressure in the non-swirl attracting pressure region is an intermediate pressure, it is lower than the pressure (discharge pressure) in the space separated by the seal on the inner peripheral side. For this reason, when the seal is broken for any reason, there is a risk that the fluid at 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 as the scroll support member,
Compressor reliability, as the scroll wraps, bearings, Oldham rings, and other sliding parts may be damaged by the destruction of the scroll wrap or, to a lesser extent, abrasion powder from the abrupt wear of the tooth roots. However, there was a problem that was reduced.

[0005] Further, since seals are provided at two locations on the inner peripheral side and the outer peripheral side of the ring-shaped non-swirl pulling pressure region, the incorporation of a seal requiring even more careful attention is required. When forming the pressure region, two seals must be incorporated almost simultaneously, and there is a problem that the assemblability is low.

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

It is another object of the present invention to provide a scroll compressor having improved part workability.

[0008]

SUMMARY OF THE INVENTION An object of the present invention is to provide a non-orbiting scroll member having a scroll wrap on a head plate and capable of moving in the axial direction without rotating, and a wrap on the head plate which meshes with the wrap of the non-orbiting scroll member. And, in a scroll compressor having a orbiting scroll member that orbits by a drive shaft, a pressure for attracting both scroll members to the non-lap side of the non-orbiting scroll member and the anti-lap side of the orbiting scroll member is increased. This is achieved by providing a means for introducing.

The object is to provide a non-orbiting scroll member having a scroll wrap on a head plate and capable of moving in the axial direction without rotating, and a wrap on a head plate engaging with the wrap of the non-orbiting scroll member. A scroll compressor having a orbiting scroll member that makes orbital motion by means of a pressure introducing means for attracting both scroll members to the non-lap side of the non-orbiting scroll member and the anti-lap side of the orbiting scroll member. This is achieved by providing a working chamber in the middle of compression and a valve provided in a hole communicating with the outside.

Another object of the present invention is to provide a revolving scroll member having a head plate and a scroll wrap, the revolving scroll member having a mirror plate and a scroll wrap and rotating without rotating in a plane perpendicular to the axial direction. In a scroll compressor having a non-orbiting scroll member in which a compression chamber is formed by being meshed and which is allowed to move in the axial direction, the scroll compressor opposes a separating force in a direction in which the scroll members are separated in the axial direction. Means for applying a pulling force in a direction of pulling the scroll members in the axial direction to each of the scroll members, and a reaction force of a biasing force which is a sum of the pulling force and the separating force. A scroll support member to be generated in each of the scroll members, and an attractive force applying means provided on a non-orbiting scroll member among the attractive force applying means. This is achieved by providing a non-swirl attracting area that has a pressure equal to or higher than the pressure of the non-swirl attracting peripheral area, which is a peripheral area surrounding the non-swirl end face, which does not include the discharge port, on the back side of the end plate. .

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of the compressor, and FIG. 2 is the same longitudinal sectional view, but a section different from FIG. In FIG. 2, only the portions not appearing in FIG. 1 are marked. FIG. 3 is an enlarged cross-sectional view near the compression chamber, and FIG.
Is an enlarged cross-sectional view of the vicinity of a ring groove forming a non-swirl attracting pressure region, FIG. 5 is a cross-sectional view of a ring seal as an elastic seal,
6 is a longitudinal sectional view of the check valve, FIG. 7 is a plan view of the check valve, FIG. 8 is a plan view of the retainer, and FIG. 9 is a non-orbiting scroll member equipped with the check valve and the ring seal. FIG. 10 is a top view of the discharge cover,
FIG. 11 is an enlarged sectional view of the back pressure valve. In this example,
The diameter of the compressor is 5mm to 1
It is of the order of 000 mm and is a low-pressure chamber system in which the suction pressure is applied to the inside of the compressor case.

First, the structure will be described. The orbiting scroll member 3 has 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 turning oil groove 3c is provided on the thrust surface 3d.

The non-orbiting scroll member 2 has a scroll wrap 2b and rotation stoppers 2g, 2h (2h
Is disposed integrally with a portion that does not become a seal portion on the outer line side of the outermost peripheral portion of the scroll wrap 2b), and the non-rotation reference surface 2u that is the same surface as the scroll wrap tooth bottom surface.
(See Fig. 2). The rotation stoppers 2g and 2h are fitted into grooves provided in the non-orbiting holder 6 and are provided with a non-orbiting scroll.
This prevents rotation of 2. In addition, rotation stop 2g,
2h may be any one of these.

Then, the bypass hole 2e and the discharge hole 2d are opened. A ring groove 2j is provided around the upper surface of the end plate 2a and communicates with a space 2f in the end plate in which the discharge hole 2d is opened by one or a plurality of pressure equalizing flow paths 2i. 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 is realized. In this embodiment, it is a single oblique hole,
There is a specific effect that the number of processing steps can be further reduced and higher productivity can be realized. Alternatively, a horizontal hole may be formed from the outer periphery of the non-orbiting scroll member 2 to close the outer flange. In this case, drilling becomes easy.
When the number of pressure equalizing flow paths 2i is one, the number of machining steps is small and mass productivity can be improved, and gas does not flow through the non-swirl attracting pressure region 29. This has the specific effect of being suppressed and improving performance. Conversely, when there are a plurality of equalizing pressure channels 2i, pressure is introduced into the non-swirl attracting pressure region 29 instantaneously, which has the effect of facilitating startup.

A check valve 24 (see FIGS. 6 to 9) including a check valve plate 24a and a retainer 24b is provided 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 excessive compression 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 insufficient compression. Retainer 24
b serves as a valve stopper when these valves open, and has the effect of suppressing fluttering of the valves.

A ring seal 22, which is an elastic seal having a U-shaped cross section made of an elastic material such as plastic, spring material or rubber, is inserted into the ring groove 2j of the non-orbiting scroll member 2. (See FIGS. 4 and 5). Here, the height of the seal is smaller than the depth of the ring groove 2j, and the inner peripheral wall is 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 closing the equalizing flow path 2i. Further, as shown in FIG. 5, a seal spring 22 having a semicircular cross section is provided in the ring seal 22.
a is inserted. When the ring seal 22 is inserted into the ring groove 22j, the seal spring 22a functions to press the inner and outer peripheral walls of the ring seal 22 against the inner wall of the ring groove 2j. By 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 equalizing flow path 2i is formed by forming a horizontal hole in the non-rotating head plate 2a, and is substantially perpendicular to 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. When a hole is formed and the outer peripheral portion of the horizontal hole is closed, even if the ring seal is lowered, the equalizing flow path 2i will not be closed, and the reliability will be improved.

As described above, since the sealing portion of the non-orbiting pulling pressure region 29, which requires careful attention to assembly, can be performed at the time of sub-assembly of the non-orbiting scroll member 2, the seal check after assembly and the In the case of a defect, reassembly becomes easy, and there is an effect that assemblability can be greatly improved.

The Oldham ring 5 is provided with non-rotating projections 5a and 5b on one surface, and is provided with turning projections 5c and 5d on the other surface as shown in FIG. The cylindrical non-orbiting holder 6 has a terrace portion 6a projecting from the center hole and supporting the non-orbiting scroll member 2, and the upper surface thereof serves as a non-orbiting support surface 6b. The upper inner peripheral surface serves as a guide surface 6c serving as a guide when the non-orbiting scroll member 2 moves up and down. Further, two radiation grooves 6d and 6e are provided on the terrace portion 6a so as to be opposed by 180 degrees about the center axis of the guide surface. The upper portions of these grooves insert the rotation stoppers 2g and 2h of the non-orbiting scroll member 2, and the lower portions are the non-orbiting projections 2 of the Oldham ring 5.
a, 2b play the role of an Oldham groove that slides.

The radial grooves 6d and 6e serve to prevent the rotation of the Oldham ring 5 by inserting the non-rotating projections 5a and 5b of the Oldham ring 5, and the rotation stopper 2g of the non-rotating scroll member 2. 2h also has a role of preventing 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 due to the orbiting motion of the orbiting scroll member 3. If these rotations are to be prevented by using different grooves, the positions where the respective grooves are dug must be made with high precision. However, in the present embodiment, since the grooves for both rotation stop are also used, positioning can be performed without having to consider the accuracy of the grooves so much. That is, since both receive the force to be rotated in the same direction, the pressure receiving surface on the groove side is the same for both the non-orbiting scroll member 2 and the Oldham ring 5. Therefore, processing accuracy is not so required for the surface that is not the pressure receiving surface of the groove.

The frame 4 has a holder mounting surface 4b for mounting the non-orbiting holder 6 on the outer peripheral portion 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 lubricating the thrust bearing portion and lubricating the suction chamber. In addition, one or a plurality of suction ports 4e through which the suction gas flows through the frame 4 in the axial direction are provided. This may be a notch on the outer periphery of the frame, or may be provided in the non-swirl holder 6.
A main bearing 4d for rotatably supporting the shaft is provided at the center. An oil discharge passage is provided from 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 thereof. This 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 10 is inserted so that it becomes a compression spring.
f is fixed to the inlet of the back pressure valve cylinder 4g.

Returning to FIG. 1, the shaft 8 is provided therein with a shaft oil supply hole 8a, a main bearing oil supply hole 8b, and a sub bearing oil supply hole 8c. On the upper part, the spindle part 8 having an enlarged diameter is provided.
h, in which a swivel bearing 8f is provided. 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 rotor balances 15a and 15b are provided at both ends.

The stator 16 is provided with a stator groove 16a (FIG. 2) at an outer peripheral portion for allowing oil to flow down to the bottom of the case. By the way, a coil through-hole is opened on the outer peripheral side of the hole through which the coil passes, and a gas flow or oil is passed therethrough.
6 may be cooled.

The sub-bearing lubrication section 9 includes a pump cover 9c having a floating bearing bush 9a having a cylindrical inner periphery and a spherical outer periphery, a sub-bearing lubrication cylinder 9b, and a lubrication pipe 9d.
Consists of The countershaft refueling 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 a support portion of the shaft 8 in the axial direction, is arranged at the upper center thereof. An eccentric circular dug 9f into which the inner rotor 26a and the outer rotor 26b of the trochoid refueling pump 26 enter is provided in the lower part thereof. This is not limited to the trochoid refueling pump, but may be another type of refueling pump.

The case comprises 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. Sub-bearing lubrication support plate 1 that supports lubrication unit 9 and has a hole through which oil passes around
8 is fixed.

Other main components include a non-swiveling press 7 for holding the ring seal 22 and a mounting member 1 for fixing the frame 4 to the cylindrical case 21.
1. There are a magnet 12 for removing iron powder in oil, a hermetic terminal 13 for supplying electric power to a motor 17, and a suction pipe 14.

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 mounted thereon by inserting the orbiting protrusions 5c and 5d into the Oldham grooves 3g and 3h, and the non-orbiting scroll member 2 is placed on the non-orbiting holder 6 above the radial grooves 6d and 6e. Is mounted so that the rotation stoppers 2g and 2h can be inserted into it. At this time, the radiation groove 6d,
The non-swirl protrusions 5a and 5b are inserted into the lower part of 6e, and the non-swivel reference surface 2u is brought into contact with the non-swivel support surface 6b. Then, the non-swirl holder 6 is fixed to the frame 4 with a screw at a position where the rotational torque is minimized while rotating the shaft 8. Then, the non-turning press surface 7a of the non-turning presser 7 is fixed to the upper surface of the non-turning holder 6 with a screw so as to cover the outer periphery of the non-turning scroll member 2 and the ring seal 22. As a result, a ring-shaped non-swirl pulling pressure region 29 is defined by the non-swirl 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 configured such that the upper edge of the ring groove 2j and the non-orbital pressing surface when viewed from within the non-orbital pulling pressure region 29. It is arranged so as to cover the boundary of the non-swirl attracting pressure region, which is the boundary with 7a. At this time, the distance between the upper surface of the non-orbiting scroll member 2 and the non-orbiting pressing surface 7a is 20 to
The maximum separation distance in the axial direction between the orbiting scroll member 3 and the non-orbiting scroll member 2 is defined so as to be about 100 μm. 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-swirl end plate 2a facing the discharge port 2d and the bypass hole 2e, and the end plate 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. Further, the discharge pipe 25
Is annealed. This is the discharge pipe 2
This is because, when the upper case 19 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 posture of the non-orbiting scroll member 2 from shifting. As described above, the compression chamber 33 is formed between the two scroll members, and the turning back space 34 is formed between the thrust surface 3d and the turning shaft 3e at the back of the turning scroll member 3. Further, the mounting member 11 is fixed to the outer peripheral portion of the rear surface of the frame 4 by screwing or caulking.

Next, the stator 16 is shrink-fitted or press-fitted in advance and the auxiliary bearing lubrication support plate 18 is
Is inserted into the cylindrical case 21 into which is welded or press-fitted. At this time, the motor wire 16 of the stator 16
c through the groove on the side of the assembly to the top. Then, tack welding is performed on the side surface of the mounting member 11. Compared to the case where tack welding is performed with the frame 4 and the non-swirl holder 6, their deformation can be avoided. Also,
A motor 17 is provided by the rotor 15 and the stator 16.
The auxiliary bearing lubrication support plate 18 and the frame 4
The motor chamber 30 is formed between them.

Next, the non-slewing lubrication member 9 is attached to the shaft 8 protruding from the hole at the center of the sub-bearing lubrication support plate 18.
Of the floating bearing member 9a. Then, the outer rotor 26b is inserted into the auxiliary bearing refueling cylinder 9b, and the inner rotor 26a is press-fitted into the end of the shaft 8. In this state, while rotating the shaft 8 and detecting the rotational torque, the position of the sub-bearing refueling cylinder 9b is adjusted, and the outer periphery of the sub-bearing refueling 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 oil supply cover 9c to which the oil supply pipe 9d is attached 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. Further, the upper case 19 is connected to the inner terminal of the discharge hermetic terminal 13 by the motor wire 16.
c, the vertical portion 25a of the discharge pipe 25 is passed through the discharge pipe outlet 19a, and then mounted and welded to the upper part of the cylindrical case 21 to form a non-swirl back chamber 32. In this state, a current is applied to the stator 16 to magnetize the permanent magnets inside the rotor 15 to form the motor 17. Then add the oil.

Next, the operation will be described. First, the flow of the compressed gas will be described. The shaft 17 is rotated by rotating the motor 17, and the orbiting scroll member 3 is caused to orbit while the Oldham ring 5 prevents rotation. The 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 compressed.
d, and is discharged into the end plate space 2f, and finally exits the compressor through the discharge pipe 25. Under the over-compression condition, in parallel with this, the endoscope space 2f passes through the bypass hole 2e and the bypass valve portion of the check ring 24.
Is discharged. As a result, the inner space 2f of the head becomes a discharge pressure. Furthermore, the upper part is the non-swirl back chamber 3 of suction pressure.
2 to form a non-swirl back center region where suction pressure is applied. Since the suction pressure is applied to the central region of the non-swirl rear surface, the deflection of the non-swirl end plate 2a is reduced, and the gap between the roots of the tooth tips can be reduced, thereby improving the energy efficiency. The pressure in the non-swirl pulling pressure region 29 defined by the ring groove 2j and the ring seal 22 can be easily adjusted to the discharge pressure by the pressure equalizing channel 2i. The entire area around the non-swirl attracting pressure area 29 is a suction pressure space. That is, since the inner peripheral side of the ring seal 22 communicates with the non-swirl rear chamber 32 and the outer periphery communicates with the suction chamber 35 or the non-swirl rear chamber 32, the pressure becomes a suction pressure. For this reason, since the pressure in the non-swirl attracting pressure region 29 is the highest pressure inside the compressor, even if the seal is broken, the pressure in the non-swirl attracting pressure region 29 does not increase, and the non-swirl attracting pressure region 29 does not increase. Scroll member 2 and orbiting scroll member 3
The attraction force, which is the force acting in the direction of contacting (attaching) each other, does not become excessive.

That is, the non-orbiting attracting area in which the pressure is equal to or higher than the non-orbiting attracting peripheral area, which is a peripheral area surrounding the non-orbiting scroll head, on the rear side of the non-orbiting scroll member that does not include the discharge port, is provided on the rear side of the non-orbiting scroll member. As a result, the pressure in at least one non-swirl attracting area is equal to or higher than the pressure in all surrounding non-swirl attracting areas, so that even if the seal there is broken, the surrounding pressure generates an attractive force. In the prior art in which the pressure is higher than the pressure in the space, the attraction force increases when the seal is broken, whereas the pressure in the non-swirl attracting region does not increase. As a result, there is an effect that a decrease in the reliability of the compressor due to an increase in the attraction force of the non-orbiting scroll, which is a problem of the related art, is suppressed.

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 the transient operation up to the steady operation, the pressure in all the non-swirl attracting regions can be maintained at or above the pressure in the non-swirl attracting region. It 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 which is the highest pressure in the compressor, the volume of the non-swirl attracting region is substantially minimized. Thus, the length of the boundary of the non-swirl attracting pressure region is generally reduced, so that the risk of leakage from the non-swirl attracting region can be reduced.
As a result, the danger of lowering the attraction force can be reduced, so that the original performance can be surely realized.

As a result, it is possible to avoid the breakage of the terrace 6a of the non-swirl holder 6 on which the urging force acts. Even if the scroll wrap does not lead to damage, the wear of the scroll wrap due to the bending and the risk of breakage in the contact with the tooth tip root can be suppressed. Further, the ring seal 22 is to be opened right and left due to the pressure difference, so that 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 of the non-swirl pulling pressure region which is the boundary between the upper edge of the ring groove 2j and the non-swirl pressing surface 7a when viewed from the inside of the non-swirl pulling pressure region 29. For this reason, it is possible to seal two places of the non-swirl pulling pressure region 29 on the inner peripheral side and the non-swirl pulling pressure peripheral region on the outer peripheral side. Conventionally, two seals are provided in each of the two places, so that even one seal requires careful attention, and two seals are installed almost at the same time when the non-swirl pulling pressure area is formed. In comparison, there is an effect that the assemblability can be greatly improved.

That is, since the pressure in the non-swirl attracting pressure region is higher than the pressure in the non-swirl attracting pressure peripheral region, the elastic seal is pressed against the non-swirl attracting pressure region boundary side, and the elasticity of the elastic seal is applied. Deforms so as to cover the entire non-swirl attracting pressure boundary. As a result, the sealing of the non-swirl pulling pressure region and the non-swirl pulling pressure peripheral region is further ensured, and there is an effect of improving the reliability and performance of the compressor. Further, since the non-swirl pulling pressure region can be formed by one seal, there is an effect that assemblability can be improved.

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

Since the non-slewing support surface 6b of the non-slewing holder 6 is arranged below the non-slewing head 2a
This has the effect of suppressing the deformation of the substrate and greatly increasing the energy efficiency. The ring seal 22 is lifted upward by the same force as the attraction force, but is stopped by the non-turning presser 7. Further, since the non-swirl rear chamber 32 has a suction pressure, the pressure inside the case of the compressor becomes the suction pressure in the entire region. As a result, the hermetic terminal 13 may be provided at any part of the case, which has a specific effect of improving manufacturability.

At the outlet of the discharge hole 2d, there is provided a central valve body 24c at the center of the check valve 24, which functions as a check valve and a discharge valve (see FIGS. 6 to 9). ). This is supported by the three valve legs 24d, and the neutral position is a position away from the conical surface above the discharge hole 2d and substantially in contact with the retainer 24b. As a result, the gas can be discharged without pushing up the central valve body 24c during the over-compression operation or the appropriate pressure ratio operation, so that there is a special effect that the discharge flow path resistance is extremely small and the performance is improved. Also, at the time of backflow from the inner space 2f of the mirror slope to the discharge hole 2d due to insufficient compression, the central valve element 24c closes the discharge hole 2d by the fluid force, so that the swelling of the acupressure diagram due to the backflow is eliminated and the performance is improved. There is a unique effect. Further, since the central valve element 24c close to the conical discharge hole 2d is used, there is also an effect that the re-expansion loss can be suppressed and the performance is improved. As described above, the discharge valve appears only when the discharge valve is necessary, and has a unique effect that extremely high efficiency can be realized at all pressure ratios of the operation. In addition, when the compressor is stopped, the central valve element 24c closes the discharge hole 2d by the fluid force at the time of the reverse flow from the inside of the mirror slope 2f to the discharge hole 2d when the compressor is stopped, so that the reverse rotation of the orbiting scroll member 3 can be suppressed. is there.

As described above, the single check valve 24 serves as a bypass valve, a discharge valve, and a check valve.
There is a specific effect that the number of parts can be suppressed and mass productivity is improved. In addition, since the structure of the valve portion can be formed by bending a single plate and outsert molding the plastic central valve body 24c, there is a specific effect that mass productivity is improved. .

Further, a conformable film (not shown) is provided on the front side of the scroll wrap 3b and the revolving end plate 3a of the revolving scroll member 3. This allows
As described above, it is possible to avoid an increase in the gap due to an error in the dimension of the part that determines the root gap of the tooth tip due to the familiarity, so that there is an effect that the energy efficiency can be further improved.

Next, the flow of the oil will be described. The oil in the oil storage chamber 31 is sucked up from the oil supply pipe 9d by the trochoid type oil supply pump 26 provided at the lower end of the shaft 8, and enters the shaft oil supply hole 8a. Here, a small amount of oil is supplied to the shaft thrust surface 9e through a gap between the upper surface of the inner rotor 26a and the circular dug 9f. The oil is supplied to the spherical bearing portion 9g on the outer periphery of the floating bearing bush 9a and flows out to the lower portion of the motor chamber 30. afterwards,
The oil returns to the oil storage chamber 31 from an oil hole 18a in the outer peripheral portion of the auxiliary bearing oil supply support plate 18. First, part of the oil that has entered the shaft oil supply hole 8a enters the auxiliary bearing oil supply hole 8c.
Oil is supplied to the cylindrical bearing of the floating bearing bush 9a. The oil then enters the motor chamber 30 via the spherical bearing 9g or directly, 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 rises through the shaft oil supply hole 8a and enters the main bearing oil supply hole 8b to supply the main bearing 4d and the slewing bearing 8f. The main shaft portion 8h is provided with the oil supply spiral groove 8i, and the amount of oil supply to the main bearing is determined by the screw pump action. Other amounts flow through the slewing bearing 8f. An oil supply groove 8j is provided therein, which serves as an oil reservoir for supplying oil to the entire area of the slewing bearing. These refueled oils flow into the swirl rear space 34. Here, since the back pressure valve 10 is provided, the pressure in the turning back space 34 becomes 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 closed by the side surface of the back pressure valve body. As a result, no oil is discharged from the swirl rear space 34, and the pressure there rises. This pressure (hereinafter referred to as back pressure) is applied 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 moves the back pressure valve body 10a to the cap 10f side. When the back pressure increases until the movement reaches the position where the oil passage groove 10e is applied to the oil inflow passage 4h, the oil passage 10g at the bottom of the oil passage groove 10e and the oil in the valve cap 10f are removed. Discharge path 10
i, a passage for oil is formed from the swirl back space 34 to the side surface of the frame 4, and oil passes through the swirl back space 34.
And the back pressure stops rising. in this way,
The back pressure is controlled to a pressure higher than the suction pressure which is the pressure on the side surface of the frame 4 by a certain value. When pressure is introduced into the back pressure detection space 10d, the back pressure valve body 10a moves rightward in the drawing against the spring force. At this time, if the pressure of the lubricating oil guided to the swirl rear space suddenly rises for some reason, the oil passage groove 10
The pressure e in the swirl back pressure space 34 remains high unless the pressure e in the swirl back pressure space 34 drops to the right after passing through the oil inflow passage 4h. Therefore, in the present embodiment, since the opposite back pressure detecting space 10d side of the back pressure valve body 10a abuts on the top of the valve cap 10f, even if the pressure in the turning back pressure space 34 rises sharply, the oil passage groove 10e and the oil It stopped at the position where the inflow path 4h opposes. As a result, the back pressure is reliably controlled to a pressure higher than the suction pressure, which is the pressure on the side surface of the frame 4, by a fixed value.

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

In FIG. 3, the thrust bearing 4
Since the oil throttle channel connecting the swirl back space 34 and the suction chamber 35 is provided by the frame oil groove 4c of FIG. 4A and the swirl oil groove 3c of the thrust surface 3d, the pressure difference by the back pressure valve is An oil path that flows into the suction chamber 35 while refueling the thrust surface is also formed. Thereby, in addition to the effect of improving the reliability of the thrust bearing and improving the performance by reducing the friction coefficient, there is also the effect of improving the performance by improving the sealing property in the compression chamber 33.

The oil discharged to the side of the frame then flows downward along the inner wall of the cylindrical case 21, and the outer peripheral groove 11 of the mounting member 11
a, finally flows into the oil storage chamber 31 through the stator outer circumferential groove 16a. In addition, the turning back space 3
Since the intermediate pressure of No. 4 does not need to be supplied from the outside, there is also a specific effect that the usability is improved.

Here, the embodiment in which the suction pressure in the case is set as the suction pressure and the pressure in the non-swirl pulling pressure region is set as the discharge pressure is shown. Should be high. For example, the suction pressure may be inside the case, and the pressure in the non-swirl pulling pressure region may be an intermediate pressure. Also,
The pressure inside the case may be the intermediate pressure, and the pressure in the non-swirl pulling pressure region may be the discharge pressure. Also, a plurality of non-swirl attractive pressure regions may be provided. Further, the present invention can of course be applied to a scroll compressor having a structure in which a non-orbiting scroll member is pressed against an orbiting scroll member.

The operation of the scroll compressor described above will now be described. Conventional scroll compressors
A back pressure is applied to the half wrap side of the orbiting scroll. The axially movable distance of the orbiting scroll is 50 μm or more. When the behavior when the orbiting scroll is actually operated is examined, the pressure in the left and right working chambers is determined. Oscillation may occur in the axial direction due to balance or other manufacturing errors. In such a movement, when the orbiting scroll moves in a direction in which the orbiting scroll is separated from the fixed scroll (non-orbiting scroll), the compressed fluid leaks from the high-pressure operating chamber to the low-pressure operating chamber, causing loss, and conversely, the orbiting scroll is fixed. When the scroll wrap is moved in a direction pressed against the scroll, there is a problem that the tip of the scroll wrap comes into contact with the end plate and the sliding resistance increases.

In this embodiment, an intermediate pressure higher than the suction pressure and lower than the discharge pressure is applied to the back surface of the orbiting scroll member 3, and a discharge pressure higher than the intermediate pressure is applied to the back surface of the fixed scroll member 3. Since the non-orbiting scroll 3 is restricted from moving in the axial direction by the non-orbiting holder 6 and its movable distance is kept within a range of 50 μm, even if the orbiting scroll member 3 swings in the axial direction, When the orbiting scroll moves in the direction in which both scroll members are separated from each other, the non-orbiting scroll member 2
Since the discharge pressure higher than the intermediate pressure is applied to the rear surface of the scroll member, the loss can be reduced by following the movement thereof, and the orbiting scroll member 3 moves in the direction in which the orbiting scroll member 3 contacts the non-orbiting scroll member 2. In this case, since the non-orbiting scroll member 2 is moved toward the half-non-orbiting scroll member in the axial direction, the loss due to galling can be reduced. Here, at the time of overcompression, the orbiting scroll member 3 shows a behavior of separating from the non-orbiting scroll member 2, but the non-orbiting scroll member 2 moves so as to follow this. At this time, a gap is slightly created between the scroll wrap and the end plate, and the working fluid (refrigerant) is transferred from the overcompressed compression chamber to the low pressure compression chamber.
Moves. However, at the next moment, the compression chamber is also over-compressed, and the over-compression state is not improved forever. Therefore, in the present embodiment, the pressure is released by providing the check valve 24a and allowing the working fluid to escape from the working chamber, which is a closed space.

That is, the non-orbiting scroll member 2 is operated while floating from the non-orbiting presser 7, and the orbiting scroll member 3 is operated while floating 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.

In reality, the pressure applied to the back of the non-orbiting scroll member 2 (the non-orbiting pulling pressure area 29) is the discharge pressure, and the back of the orbiting scroll member 3 (the orbiting back space 34).
Is a so-called intermediate pressure, a few μm is provided between the half wrap side surface of the orbiting scroll member 3 and the thrust surface 3d.
Only the order floats. Lubricating oil has entered this floating space. For this reason, in the axial swinging motion of the orbiting scroll member 3, the motion in the direction away from the non-orbiting scroll 2 due to the increase in the pressure in the compression chamber (overcompression) is pressed by the thrust surface 3d as a thrust bearing. .
At this time, the check valve 24a opens to release the over-compression 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
In the direction, the galling is reduced.

In the case of so-called liquid compression in which liquid refrigerant is sucked, a considerable force is applied to both scroll members, and both scroll members move in directions away from each other. Can be suppressed.

Further, in this embodiment, the low pressure chamber system in which the inside of the closed container containing the compression mechanism and the electric mechanism is used as the suction pressure has been described. The same effect is obtained in a high-pressure chamber system in which the inside is set to a discharge pressure or an intermediate pressure.

Next, a second embodiment of the ring seal 22 will be described with reference to an enlarged sectional view of the ring seal 22 in FIG. Except that the seal spring 22a is attached to the inner surface of the U-shaped ring seal 22 made of plastic, it is the same as the first embodiment, so that the description other than that point is omitted. Accordingly, even when there is no pressure difference between the inside and outside of the ring seal at the time of startup, the sealing property can be ensured by the spring force, so that the discharge gas does not flow into the swirl back space 34 or the suction chamber 35, and the startup can always be performed smoothly. This has the effect.

Next, a third embodiment of the ring seal 22 will be described with reference to an enlarged sectional view of the ring seal 22 shown in FIG. U-shaped ring seal 22 made of plastic
Seal spring 2 which presses against the inner surface of a ring groove 2j at the bottom of the ring groove 2j
Since it is the same as the second embodiment except that 2b is attached, the description other than that portion is omitted. As a result, even when the pressure difference between the inside and outside of the ring seal immediately after the start is small, the non-turning attraction force can be applied by the spring force, so that the start can be performed more smoothly.

[0057]

According to the present invention, there is an effect that a scroll compressor capable of reducing leakage loss and sliding loss can be provided.

Also, there is an effect that a scroll compressor with improved part workability can be provided.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment.

FIG. 2 is another longitudinal sectional view of the first embodiment.

FIG. 3 is an enlarged cross-sectional view of the vicinity of a compression chamber of the first embodiment.

FIG. 4 is an enlarged cross-sectional view of the vicinity of a ring groove of the first embodiment.

FIG. 5 is a sectional view of the ring seal of the first embodiment.

FIG. 6 is a longitudinal sectional view of the check valve body of the first embodiment.

FIG. 7 is a plan view of the check valve body of the first embodiment.

FIG. 8 is a plan view of the retainer of the first embodiment.

FIG. 9 is a top view of the non-orbiting scroll member according to the first embodiment at the time of a subassembly in which a check valve and a ring seal are mounted.

FIG. 10 is a top view of the ejection cover according to the first embodiment.

FIG. 11 is an enlarged sectional view of the back pressure valve of the first embodiment.

FIG. 12 is an enlarged sectional view of a ring seal according to a second embodiment.

FIG. 13 is an enlarged sectional view of a ring seal according to a third embodiment.

[Explanation of symbols]

2 ... non-orbiting scroll member, 2j ... ring groove, 3 ... orbiting scroll member, 4 ... frame, 5 ... Oldham ring,
6 Non-rotating holder, 8 Shaft, 10 Back pressure valve, 22
... ring seal, 24 ... check valve, 26 ... oil pump, 29 ... non-swirl pulling pressure area, 33 ... compression chamber, 34 ... swirl back space.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masahiro Takebayashi 800, Tomita, Oji, Ohira-cho, Shimotsuga-gun, Tochigi In-house cooling and cooling division, Hitachi, Ltd. (72) Inventor Yugo Mukai 800 Tomita, Ohira-cho, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture F-term (ref.) CC29 CC31 CC35

Claims (7)

[Claims] 1. A non-orbiting scroll member having a scroll wrap on an end plate and capable of moving in the axial direction without rotating, and a wrap on the end plate meshing with the wrap of the non-orbiting scroll member, wherein a slewing motion is performed by a drive shaft. A scroll compressor having a means for introducing pressure for attracting both scroll members to the non-lapping side of the non-orbiting scroll member and the non-lapping side of the orbiting scroll member. Machine. 2. A non-orbiting scroll member having a scroll wrap on an end plate and capable of moving in the axial direction without rotating, and a wrap on the end plate meshing with the wrap of the non-orbiting scroll member, wherein the orbiting motion is performed by a drive shaft. And a means for introducing pressure to attract both scroll members to the non-lap side of the non-orbiting scroll member and to the anti-lap side of the orbiting scroll member. A scroll compressor comprising a working chamber and a valve provided in a hole communicating the outside. 3. An orbiting scroll member having a head plate and a scroll wrap and rotating without rotating in a plane perpendicular to the axial direction, a head plate and a scroll wrap, and being compressed by being engaged with the orbiting scroll member. A scroll compressor having a non-orbiting scroll member in which a chamber is formed and which is allowed to move in the axial direction, wherein the two scroll members are opposed to a separating force in a direction of separating the two scroll members in the axial direction. Attraction force applying means for applying an attraction force in the axial direction to each of the scroll members, and a reaction force of an urging force which is a sum of the attraction force and the separation force to each of the scroll members. A scroll support member to be generated;
The attraction force applying means provided on the non-orbiting scroll member of the attraction force applying means is provided on the outer peripheral side of the non-orbiting scroll rear surface not including the discharge port on the rear side of the end plate of the non-orbiting scroll member. A scroll compressor having a non-swirl attracting region in which pressure is equal to or higher than a non-swirl attracting peripheral region that is a region. 4. The scroll compressor according to claim 3, wherein the pressure in the non-orbiting attraction pressure region is a discharge pressure. 5. The scroll compressor according to claim 3, further comprising: a pressure equalizing flow path communicating between the non-orbiting attraction pressure region and the center of the non-orbiting scroll plate rear surface including a discharge port on the mirror plate rear surface side of the non-orbiting scroll member. . 6. The non-swirl attractive pressure region according to claim 3, wherein the non-swirl attractive pressure region is a boundary between the non-swirl attractive pressure region and the non-swirl attractive pressure peripheral region. A scroll compressor having an elastic seal that covers the boundary of the orbiting pressure region and does not cover the pressure introduction port that introduces pressure into the non-orbiting pressure region. 7. The non-swirl pulling pressure region according to claim 6, wherein the non-swirl attracting pressure region is formed by a ring groove formed around the discharge port on the back side of the non-swirl end plate, and a seal support disposed to cover the ring groove. A scroll compressor which is partitioned and has such a shape and arrangement that the elastic seal is in contact with at least three inner and outer peripheral surfaces of the ring groove and the seal support surface in the non-orbital drawing pressure region.