JP4477182B2 - Scroll compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scroll compressor, and is suitable for a scroll compressor that supports a non-orbiting scroll member with a support member separate from the orbiting scroll member.
[0002]
[Prior art]
As a conventional scroll compressor of this type, as disclosed in Japanese Patent Application Laid-Open No. 7-189934, an orbiting scroll member having an end plate, a spiral scroll wrap standing on the end plate, an end plate and an erecting scroll member are provided. A non-orbiting scroll member having a spiral scroll wrap that is allowed to move in the axial direction, a compression chamber that is formed by meshing both scroll members and that is substantially closed to reduce the volume, and fluid on the compression chamber side Non-orbiting attraction applied to the non-orbiting scroll member in a direction to attract the end plate of the non-orbiting scroll member against the non-orbiting pulling force in the direction of separating the end plate of the non-orbiting scroll member due to the pressure of A non-orbiting scroll that generates a reaction force of the non-orbiting biasing force, which is a vector sum of the non-orbiting attraction force and the non-orbiting attraction / separation force, on the non-orbiting scroll member. The non-orbiting attraction force adding means applies a discharge pressure to the central portion of the back surface of the non-orbiting scroll member, and the direction of the non-orbiting biasing force toward the orbiting scroll member during normal operation. There is a non-orbiting pulling force of a magnitude such that the non-orbiting support member is formed separately from the orbiting scroll member and supports the peripheral portion of the non-orbiting scroll member.
[0003]
[Problems to be solved by the invention]
However, such a conventional scroll compressor applies a discharge pressure to the center of the back surface of the non-orbiting scroll member by the non-orbiting attractive force adding means, and the non-orbiting biasing force is directed toward the orbiting scroll member during normal operation. Therefore, if the non-orbiting scroll member is surely biased against the orbiting scroll member even under various operating conditions including a transient state, the non-orbiting scroll member has a large non-orbiting force. It is necessary to apply an attractive force. For this reason, during normal operation such as rated operation, it is necessary to have a non-orbiting attraction force that applies a non-orbiting attraction force much larger than the pulling force, and the non-orbiting scroll member has a large non-orbiting biasing force. Occurs, and the central portion of the non-orbiting scroll member is greatly deformed to the orbiting scroll member side.
[0004]
For example, when the frequency is very high, the suction pressure is high but the discharge pressure is not increased, so that the pulling force is large and the pulling force is small. In particular, in the case of a compressor not provided with a bypass valve for suppressing overcompression, the separating force becomes very large. Even in such a case, it is necessary to ensure that the attractive force is equal to or greater than the pulling force. Otherwise, the non-orbiting scroll cannot be attracted to the orbiting scroll, and normal compression may not be achieved due to the enlargement of the tooth tip bottom gap. For this reason, it is necessary to increase the non-orbiting pulling force of the non-orbiting scroll member by setting a wide area where the discharge pressure is applied. As a result, in the normal operation where the suction pressure is lower and the discharge pressure is higher than at the time of startup, the non-orbiting urging force becomes very excessive, and the central portion of the non-orbiting scroll member is greatly deformed.
[0005]
Here, the deformation | transformation state which applied the discharge pressure in the wide area | region to the back center part of the non-orbiting scroll member is demonstrated using FIG. FIG. 9 is an explanatory diagram schematically showing a deformed state during normal operation in which discharge pressure is applied to a non-orbiting scroll member of a conventional scroll compressor in a wide area.
[0006]
A thin two-dot chain line in FIG. 9 indicates the shape of the non-orbiting scroll member before deformation. Further, the concentration force distributed on the line is indicated by a large arrow, and the distribution force distributed in a plane, that is, the pressure is indicated by a small arrow. Furthermore, the length of this arrow has shown the magnitude | size on the basis of suction pressure, and the location without an arrow represents that suction pressure is acting. These points are the same in each figure described below.
[0007]
As is apparent from FIG. 9, a non-orbiting attractive force indicated by a thin solid line is applied to a wide area at the center of the back surface of the non-orbiting scroll member. The non-swivel pulling force indicated by a thin dotted line due to the pressure of the fluid on the compression chamber side is applied to the region. As a result, the non-orbiting scroll member generates a non-orbiting biasing force indicated by a thick solid line that is the vector sum of the non-orbiting attraction force and the non-orbiting attraction / separation force. Will be transformed. That is, a non-orbiting urging reaction force is generated at the inner periphery of the non-orbiting support member and receives a non-orbiting urging force. The non-orbiting scroll member has a bending moment with the inner periphery of the non-orbiting support member as a fulcrum. Will occur and will be greatly deformed.
[0008]
Moreover, the deformation | transformation state by the pressure and temperature of the fluid of the compression chamber of a non-orbiting scroll member is demonstrated using FIG. FIG. 10 is an explanatory diagram schematically showing the deformation state of the non-orbiting scroll member of the conventional scroll compressor due to the pressure and temperature of the fluid in the compression chamber.
[0009]
As apparent from FIG. 10, the compression chamber on the outer peripheral side has a higher pressure than the compression chamber on the central side of the scroll wrap of the non-orbiting scroll member, so that a gas force is applied from the central side to the outer periphery perpendicular to the wrap side surface. . As a result, a bending moment is generated at the base of the scroll wrap, and the non-orbiting scroll member is rotated in the same direction as the deformation shown in FIG. This deformation is small in a normal scroll wrap, but becomes large when the scroll wrap is high and cannot be ignored. Further, since the gas in the compression chamber on the center side becomes high temperature due to compression close to heat insulation, the scroll wrap of the non-orbiting scroll member extends in the center due to thermal expansion.
[0010]
The sum of the deformation amount and the thermal expansion shown in FIGS. 9 and 10 is the deformation amount of the non-orbiting scroll member. However, since the deformation is performed in the same direction, the deformation is very large. As a result, a large displacement occurs between the tooth tip and the tooth bottom of the non-orbiting scroll member.
[0011]
As described above, in the conventional scroll compressor, the deformation of the non-orbiting scroll member cannot be suppressed in a wide operation range, and the deformation of the non-orbiting scroll member during the normal operation becomes large. The internal leakage from the gap between the tooth tip and the tooth bottom of the scroll wrap of the scroll member becomes large, leading to a decrease in energy efficiency.
[0012]
The object of the present invention is to suppress the deformation of the non-orbiting scroll member in a wide operating range, and by keeping the clearance between the tooth tip and the tooth bottom of the scroll wrap of the non-orbiting scroll member and the orbiting scroll member small in a wide range, It is to obtain a scroll compressor with high energy efficiency by reducing leakage.
[0013]
[Means for Solving the Problems]
In order to achieve the above object, the present invention includes an end plate and a orbiting scroll member provided with a spiral scroll wrap standing on the end plate, and an end plate and a spiral scroll wrap standing on the end plate, and is allowed to move in the axial direction. A non-orbiting scroll member, a compression chamber that is formed by meshing both scroll members and whose volume is reduced, and a direction in which the end plate of the non-orbiting scroll member is pulled apart by the pressure of the fluid on the compression chamber side. A non-orbiting attraction force adding means for applying a non-orbiting attraction force on the non-orbiting scroll member in a direction to attract the end plate of the non-orbiting scroll member against the non-orbiting pulling force of And a non-orbiting scroll support member that causes the non-orbiting scroll member to generate a reaction force of a non-orbiting urging force that is a vector sum of the non-orbiting separation force, The non-orbiting scroll member has a suction center in the back center region thereof, The non-slewing attractive force adding means is in normal operation, Providing a non-orbiting attraction pressure area on the outer periphery of the back surface of the non-orbiting scroll member to give the non-orbiting attraction force by applying a discharge pressure; The non-orbiting pulling force having such a magnitude that the non-orbiting biasing force is directed toward the orbiting scroll member is provided, and the non-orbiting pulling force having a magnitude such that the non-orbiting biasing force is directed toward the orbiting scroll member. The non-orbiting support member has at least a portion formed separately from the orbiting scroll member, and at least a part of the support surface for the non-orbiting scroll member in the portion formed separately is provided. It is formed so as to overlap with the action region of the non-swirl attractive force.
[0016]
The present invention Favor In a preferred configuration example, the non-orbiting scroll member is located at the center of the end plate corresponding to the compression chamber. Discharge pressure This is because the end plate space is formed.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol in the figure of each Example shows the same thing or an equivalent.
[0020]
First to fourth embodiments of the present invention will be described with reference to FIGS. FIG. 1 is an explanatory diagram schematically showing a deformed state during normal operation in which a non-orbiting attractive force is applied to a non-orbiting scroll member of a scroll compressor according to a first embodiment of the present invention, and FIG. FIG. 3 is an explanatory view schematically showing a deformation state during normal operation in which a non-orbiting attractive force of intermediate pressure is distributed and applied to a non-orbiting scroll member of a scroll compressor according to a second embodiment of the present invention. FIG. 4 is an explanatory diagram schematically showing a deformed state during normal operation in which a non-orbiting attractive force of discharge pressure is distributed and applied to a non-orbiting scroll member of a scroll compressor according to a third embodiment of the present invention. 4 schematically emphasizes the deformation state during normal operation in which the non-orbiting scroll force of the scroll compressor according to the fourth embodiment of the present invention is applied to the non-orbiting scroll member in a distributed manner. It is explanatory drawing shown.
[0021]
The basic configuration of the first to fourth embodiments will be described with reference to the reference numerals of the parts common to the fifth embodiment.
[0022]
This basic configuration includes an end plate 3a and a orbiting scroll member 3 provided with a spiral scroll wrap 3b standing upright thereto, and an end plate 2a and a spiral scroll wrap 2b provided upright thereto, and is allowed to move in the axial direction. The non-orbiting scroll member 2, the compression chamber 33 formed by meshing these scroll members 2 and 3 and having a substantially closed capacity to reduce the volume, and the end plate 2a of the non-orbiting scroll member 2 by the pressure of the fluid on the compression chamber side A non-orbiting attraction force applying means for applying a non-orbiting attraction force on the non-orbiting scroll member 2 in a direction for attracting the end plate 2a of the non-orbiting scroll member 2 against the non-orbiting separation force in the direction of separating A non-orbiting scroll support member 6 that causes the non-orbiting scroll member 2 to generate a reaction force of a non-orbiting biasing force that is a vector sum of the orbiting attraction force and the non-orbiting separation force; The orbiting attraction force adding means gives a non-orbiting attraction force having such a magnitude that the non-orbiting urging force is directed toward the orbiting scroll member 2 during normal operation. In addition to being formed separately, at least a part of the support surface of the outer peripheral edge of the non-orbiting scroll member 2 is formed so as to overlap the action region of the non-orbiting attractive force.
[0023]
In the first embodiment, as shown in FIG. 1, the non-orbiting attracting force applied to the rear surface of the peripheral edge of the non-orbiting scroll member 2 is a concentrated force, and the non-orbiting scroll member 2 is sucked into the central region of the rear surface. It is configured to apply pressure. Further, the support surface of the non-orbiting scroll member 2 is a support surface of the support member 6 different from the orbiting scroll member, and the position thereof is outside the orbiting range of the orbiting scroll wrap. Since the scroll wrap starts to be wound around the center of the end plate, the support surface of the non-orbiting scroll member 2 is provided on the outer periphery of the end plate 2 a of the scroll member 2. In the first embodiment, since the non-orbiting attracting force is a concentrated force, the support surface of the non-orbiting scroll member 2 is located below the portion where the non-orbiting attracting force is applied.
[0024]
As a result, as shown in FIG. 1, the force finally applied is the non-orbiting pulling force of the distributed force applied to the central portion of the end plate 2a, the non-orbiting attractive force applied to the outer periphery of the non-orbiting scroll member 2, and It can be considered that it is composed of three forces including the non-orbiting urging reaction force received on the outer periphery of the non-orbiting scroll member 2. Therefore, even during normal operation, the force that deforms the non-orbiting scroll member 2 becomes the non-orbiting pulling force applied to the central portion of the end plate 2a, and the deformation amount of the end plate 2a of the non-orbiting scroll member 2 is reduced. Further, the non-orbiting attracting force, which is a very large force, causes the outer periphery of the end plate 2a of the non-orbiting scroll member 2 to be in close contact with the non-orbiting support member 6, so that the end plate 2a is away from the non-orbiting support member 6. Becomes horizontal. Thereby, the deformation amount of the non-orbiting scroll member 2 is further suppressed.
[0025]
By the way, the direction of deformation of the end plate 2a of the non-orbiting scroll member 2 is the direction toward the counter-orbiting scroll member opposite to the direction of the conventional FIG. 9, and the tooth tip teeth on the center side of the scroll wrap 2b. The bottom gap is in an expanding direction. However, the deformation due to the gas force applied to the side surface of the scroll wrap 2b is the same as in the conventional case of FIG. 10, and these deformations cancel each other, so that the deformation of the end plate 2a of the non-orbiting scroll member 2 is further reduced.
[0026]
As a result, there is an effect that the amount of displacement between the tooth tip and the tooth bottom of the non-orbiting scroll member is reduced, the internal leakage loss is reduced, and the energy efficiency is improved. In addition, in this 1st Example, although the case where suction pressure was applied to the back center area | region of a non-orbiting scroll member was shown, the intermediate pressure between suction pressure and discharge pressure may be sufficient. In this case, the deformation of the end plate due to the axial force is further reduced.
[0027]
Further, in the second embodiment, as shown in FIG. 2, the non-orbiting attracting pressure region is entirely overlapped with the support surface when viewed from the axial direction, and suction pressure is applied to the rear central region of the non-orbiting scroll member 2. It is configured.
[0028]
In the second embodiment, the non-orbiting attracting force is a distributed force, so that the non-orbiting scroll member is compared with the first embodiment in which the non-orbiting attracting force is a concentrated force. The concentration degree of the urging reaction force applied to the non-turning reference surface that is in contact with the support surface that provides the axial reference position is reduced. As a result, together with the effects of the first embodiment, the risk of damage to the support surface of the support member and the non-orbiting reference surface of the non-orbiting scroll member is reduced, and the axial positioning of the non-orbiting scroll member can be maintained with high accuracy. In addition, there is an effect that the tooth tip bottom gap can be properly maintained and energy efficiency can be improved. In the second embodiment, the case where the suction pressure is applied to the central region of the back surface of the non-orbiting scroll member 2 is shown, but an intermediate pressure may be used. In this case, the amount of deformation of the end plate due to the axial force is further reduced.
[0029]
Further, the second embodiment is a case where the non-swirl attracting pressure region is entirely overlapped with the support surface when viewed from the axial direction. If a part of the non-swivel attracting pressure region is on the inner peripheral side of the support surface, In this case, the maximum displacement amount of the tooth tip and the tooth bottom generated in the central part of the end plate due to the axial force is reduced. In this case, the deformation of the end plate 2a of the non-orbiting scroll member 2 can be reduced when the compressor shown in FIG. 10 is small or the compressor has a small amount of thermal expansion at the center of the scroll wrap (for example, when the scroll wrap is low). This is effective for improving energy efficiency.
[0030]
On the contrary, when the inner side of the non-swirl attracting pressure region is located on the outer peripheral side from the inner side of the support surface, the deformation amount of the central part of the end plate due to the axial force further increases slightly. In this case, in the case of a compressor in which the deformation shown in FIG. 10 is extremely large or the thermal expansion amount of the scroll wrap central portion is extremely large (for example, when the scroll wrap is extremely high), the deformation of the non-rotating end plate is reduced. This is effective for improving energy efficiency.
[0031]
In the third embodiment, as shown in FIG. 3, in the second embodiment, the pressure in the non-rotating attraction pressure region is limited to the discharge pressure. Since the discharge pressure is almost the maximum pressure in the compressor, the necessary area for generating the non-swirl attractive force is minimized. As a result, as shown in FIG. 7, the area of the non-orbiting attracting pressure region can be reduced together with the effect of the second embodiment, so that the end plate 2a of the non-orbiting scroll member 2 can be reduced in diameter, and the compressor can be reduced in diameter. There is an effect that can be done.
[0032]
In the fourth embodiment, as shown in FIG. 4, an end plate internal space 2f is provided near the center of the end plate 2a of the non-orbiting scroll member 2 in the third embodiment. As shown in the enlarged view in FIG. 4, the end plate space 2 f tends to expand due to the discharge pressure of the end plate space 2 f, so that the compression chamber side portion of the end plate 2 a of the non-orbiting scroll member 2 moves downward. Causes deformation to bend. As a result, the deformation of the end plate 2a of the non-orbiting scroll member 2 due to the axial force becomes very small as shown in FIG. In addition, compared with the case where the discharge pressure is applied to the central region of the back surface of the non-orbiting scroll member 2, the anti-compression chamber side portion of the non-orbiting end plate serves as a beam, so Deflection can be suppressed. Therefore, the final deformation of the end plate 2a of the non-orbiting scroll member 2 (that is, the deformation caused by the force applied to the side surface of the scroll wrap and the deformation caused by thermal expansion shown in FIG. 10) is extremely small. The tooth tip bottom gap becomes extremely small during a wide range of operation, and leakage is suppressed, and the energy efficiency is greatly improved.
[0033]
Next, a fifth embodiment of the present invention will be described with reference to FIGS. FIG. 5 is a longitudinal sectional view of a scroll compressor according to a fifth embodiment of the present invention, and FIG. 6 is a longitudinal sectional view of different parts of the scroll compressor of FIG. In FIG. 6, symbols are attached only to portions that did not appear in FIG.
[0034]
The compressor of the fifth embodiment has a diameter of about 10 mm to 1000 mm and is of a low pressure chamber type in which the inside of the compressor case serves as a suction pressure. This low-pressure chamber type compressor is characterized in that the total amount of refrigerant sealed in the refrigeration cycle is small because the compressor internal volume that occupies a large proportion of the total volume of the refrigeration cycle is low pressure. Thereby, in the compressor using the combustible hydrocarbon refrigerant or the refrigerant containing R32 or the like, the amount of leakage can be reduced when the refrigerant leaks. In addition, when a very high-pressure refrigerant such as CO 2 is used, the pressure resistance design of the compressor case is easy.
[0035]
First, the structure of this compressor will be described.
[0036]
The orbiting scroll member 3 is provided with a scroll wrap 3b and Oldham grooves 3g and 3h (see FIG. 6) having an involute or an algebraic spiral as a basic line on the upper surface of the end plate 3a, and the thrust surface 3d and the orbit on the lower surface of the end plate 3a. A shaft 3e is provided, and a swirl oil groove 3c is provided on the thrust surface 3d thereof.
[0037]
The non-orbiting scroll member 2 is provided with a scroll wrap 2b and rotation stoppers 2g and 2h on the lower surface of the end plate 2a, and a non-orbiting reference surface 2u that is flush with the bottom surface of the scroll wrap 2b. The non-orbiting scroll member 2 is provided with a bypass hole 2e for suppressing overcompression and avoiding liquid compression so as to communicate with the middle portion of the compression chamber, and bypassing the opening of the bypass hole 2e into the sealed container. A valve 23 is provided. Further, the non-orbiting scroll member 2 is provided with a discharge hole 2d opened at the center, and a door-shaped check valve 24 for opening and closing the opening is provided.
[0038]
A rear outer peripheral groove 2j is provided on the entire peripheral edge of the upper surface of the end plate 2a, and a single pressure equalizing hole 2i that communicates the rear outer peripheral groove 2j and the end plate inner space 2f is provided. A ring seal 22 having a U-shaped cross section made of an elastic body such as plastic, spring material, or rubber is inserted into the back outer peripheral groove 2j. The height of the ring seal 22 is made smaller than the depth of the back outer peripheral groove 2j, and the inner peripheral wall thereof is shorter than the outer peripheral wall. Thereby, even if the ring seal 22 is lowered to the bottom of the rear outer peripheral groove 2j, the inner peripheral wall of the ring seal 22 can be prevented from blocking the pressure equalizing hole 2i. The discharge cover 2c is fixed to the upper surface of the end plate 2a during assembly so as to form an end plate space 2f above the opening of the discharge hole 2e.
[0039]
The Oldham ring 5 is provided with non-rotating protrusions 5a and 5b on one surface and rotating protrusions 5c and 5d on the other surface.
[0040]
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 of the terrace portion 6a is a non-orbiting support surface 6b. The inner peripheral surface of the upper portion of the terrace portion 6a serves as a guide surface 6c that serves as a guide when the non-orbiting scroll member 2 moves up and down. Furthermore, two radiation grooves 6d and 6e are provided on the terrace portion 6a so as to face each other at 180 degrees. The grooves 6d and 6e have rotation stoppers 2g and 2h of the non-orbiting scroll member 2 inserted in the upper part thereof, and the lower part serves as an Oldham groove in which the non-orbiting protrusions 5a and 5b of the Oldham ring 5 slide.
[0041]
The frame 4 is provided with 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 is provided on the inner side of the same surface. The thrust bearing 4a is provided with a plurality of frame oil grooves 4c for supplying the thrust bearing portion concentrically. The frame 4 is provided with one or a plurality of suction ports 4 e through which the suction gas flows through the peripheral edge of the frame 4 in the axial direction. A main bearing 4 d that rotatably supports the shaft 8 is provided at the center of the frame 4.
[0042]
An oil discharge passage 4f 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 is provided in the middle of the oil discharge passage 4f. The back pressure valve 10 includes a valve plate 10a, a valve spring 10b, and a valve cap 10c. The valve cap 10c and the insertion hole must be completely sealed. The valve spring 10b is compressed, and the valve plate 10a is attached so as to be pressed against the valve seal surface. Since this pressing force determines the pressure value of the back surface of the orbiting scroll member 3, it is necessary to accurately manage the shape and size related to the amount of compression of the valve spring 10b that determines this pressure value. In particular, it is necessary to finish the end portion of the valve spring 10b to a surface substantially perpendicular to the central axis of the spring. Otherwise, buckling occurs when the valve spring 10b is compressed, the orbiting back pressure value becomes abnormally small, the orbiting scroll member 3 is pressed against the frame 4, the sliding loss increases, and the energy efficiency decreases. .
[0043]
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. Further, a main shaft portion 8h having an enlarged diameter is provided at the upper portion of the shaft 8, 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 8h from the outlet of the main bearing oil supply hole 8b, and an oil supply groove 8j is provided on the swing bearing 8f.
[0044]
The rotor 15 incorporates an unmagnetized permanent magnet (not shown), and is provided with rotor balances 15a and 15b at both ends.
[0045]
The stator 16 is provided with a stator groove 16a for allowing oil to flow down to the bottom of the case on the outer peripheral portion, a coil passes through the inside, and a coil end portion 16b is provided above and below the stator groove 16a. Note that the stator 16 may be cooled by making a coil through hole on the outer peripheral side of the hole through which the coil passes and passing a gas flow or oil.
[0046]
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 a floating bearing bush 9a is incorporated therein. Furthermore, the shaft thrust surface 9e which is an axial direction support part of the shaft 8 is arranged in 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 supply pump 26 enter is provided at the lower part.
[0047]
The case is composed of three parts: an upper case 19 to which a hermetic terminal 13 and a discharge pipe outlet 19a are welded or brazed, a lower case 20, and a cylindrical case 21. A sub-bearing oil supply support plate 18 that supports 9 is fixed.
[0048]
Other main components include a non-orbiting presser 7 for holding the ring seal 22 so as to press the non-orbiting scroll member 2 downward, a mounting member 11 for fixing the frame 4 to the cylindrical case, and iron powder in oil. There are a magnet 12 that removes power, a hermetic terminal 13 that supplies power to the motor 17, and a suction pipe 14.
[0049]
Next, a method for assembling these components will be described.
[0050]
First, the shaft 8 into which the rotor 15 is press-fitted or shrink-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 Oldham ring 5 with the swiveling projections 5c and 5d inserted into the Oldham grooves 3g and 3h, and the non-turning scroll member 2 is placed on the non-turning holder 6 above the radiation grooves 6d and 6e. What is mounted so that the rotation stoppers 2g and 2h are inserted is covered from above. At this time, the non-turning protrusions 5a and 5b of the Oldham ring 5 are inserted below the radiation grooves 6d and 6e of the non-turning holder 6, 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.
[0051]
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. This may be welded or glued rather than screwed. In the case of bonding, there is a specific effect that deformation is small and management of the tooth tip bottom gap of the scroll becomes easy. 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 defined.
[0052]
Then, a discharge cover 2c having a discharge pipe 25 is closely fixed with a screw near the center of the non-rotating end plate 2a facing the discharge port 2d and the bypass hole 2e, thereby providing an end plate space 2f. In addition, you may fix the discharge cover 2c via a sealing material. Thus, since the end plate space 2f is formed by fixing the discharge cover 2c, there is no need to form a space through the end of the end plate 2a, and there is a specific effect that processing is easy. Further, the discharge pipe 25 attached to the fixed cover 2c behaves as an elastic body within a range movable up and down of the non-orbiting scroll member 2, and as a result, the non-orbiting scroll member 2 is elastically supported by the compressor case.
[0053]
As described above, the compression chamber 33 is formed between the scroll members 2 and 3, and the orbiting back space 34 is formed between the thrust surface 3c and the orbiting shaft 3e on the back surface of the orbiting scroll member 2.
[0054]
Further, the mounting member 11 is fixed to the outer periphery of the back surface of the frame 4 with screws. Instead of fixing with screws, it may be fixed by caulking.
[0055]
Next, the above-described assembly component is inserted into the cylindrical case 21 in which the stator 16 is pre-fitted or press-fitted 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 part. Then, the side surface of the mounting member 11 is tack welded. By welding in this way, the deformation of these parts can be avoided as compared with the case of tack welding the frame 4 and the non-revolving holder 6, so that it exceeds the seal gap of the compression chamber 33 determined by the tolerance of the parts. The gap at the time of assembling is not enlarged, and internal leakage can be suppressed and energy efficiency is improved. 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.
[0056]
Next, the inner periphery of the floating bearing bush 9 a of the non-swivel oil supply portion 9 is inserted and attached to the shaft 8 that has come out from the hole in the center portion 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 turned to adjust the position of the sub-bearing oil supply cylinder 9b while detecting the rotational torque, and the sub-bearing oil supply support plate 18 is connected to the outer periphery of the sub-bearing oil supply cylinder 9b at the position where the rotational torque is minimized. Spot welded to. Then, the oil supply cover 9c with the oil supply pipe 9d is screwed to the auxiliary bearing oil supply cylinder 9b with a seal interposed therebetween. Here, it is possible to increase the accuracy of the seal surface and increase the pressing force of the seal surface so that the seal is performed without sandwiching the seal.
[0057]
Finally, the lower case 20 to which the magnet 12 is fixed is welded to the cylindrical case 21 to form the oil storage chamber 27. In addition, the motor wire 16c is attached to the inner terminal of the discharge hermetic terminal 13 of the upper case 19, the vertical portion 25a of the discharge pipe 25 is passed through the discharge pipe outlet 19a, and the upper case 19 is placed on the cylindrical case 21. The non-turning back chamber 32 is formed by mounting and welding. 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.
[0058]
Next, the operation of the compressor will be described.
[0059]
First, the flow of compressed gas will be described.
[0060]
In order to operate the compressor, the rotor 16 is rotated by energizing the stator 16 of the motor 17 and the shaft 8 fixed to the rotor 15 is rotated. As the shaft 8 rotates, the orbiting scroll member 3 is orbited. Here, since the Oldham ring 5 is provided, rotation of the orbiting scroll member 3 is prevented.
[0061]
Due to the rotation of the orbiting scroll member 3, the gas filled in the case through the suction pipe 14 flows into the suction chamber 35 through the suction port 4 e of the frame 4, is closed and compressed in the compression chamber 33, and is discharged into the discharge hole. 2d is discharged into the end plate space 2f, and finally goes out of the compressor through the discharge pipe 25. Under the overcompression condition, the gas compressed in the compression chamber 33 and compressed is discharged into the end plate space 2f through the bypass hole 2e and the bypass valve 23 in parallel with the discharge from the discharge hole 2d. . Thereby, the space 2f in the end plate becomes a discharge pressure.
[0062]
Further, the discharge cover 2C forming the end plate space 2f has a suction pressure non-swirl back chamber 32 above it, and forms a non-swirl back center region to which the suction pressure is applied. Since the suction pressure is applied to the central region of the non-revolving back surface, the deflection of the non-revolving end plate 2a is reduced, the tooth bottom gap can be reduced, and the energy efficiency is improved. The suction port 4e may be provided in the vicinity of the compression chamber 33 starting to close. Thereby, there exists an effect which a suction flow path loss reduces and energy efficiency improves.
[0063]
The pressure inside the ring seal 22 becomes a discharge pressure by the pressure equalizing hole 2i that communicates the inner space 2f of the end plate and the inside of the ring seal 22 in the rear outer peripheral groove 2j. Seal. This is possible because all the outside of the ring seal 22 is a space for suction pressure. Thereby, the inside of the back outer peripheral groove 2j becomes a discharge pressure to form the non-swirl attracting pressure region 29.
[0064]
Since the non-swirl support surface 6b of the non-swirl holder 6 is disposed below the non-swirl attracting pressure region 29, as described in the above embodiment, the deformation of the non-swivel end plate 2a is suppressed, and during operation. Since the tooth tip bottom gap can be reduced, the energy efficiency is very high.
[0065]
Further, since the non-swirl attracting force is not a concentrated force such as a spring force but a distributed force, as described in the above embodiment, the risk of damaging the non-slewing support surface 6b and the non-swinging reference surface 2u is reduced. Since the axial positioning of the non-orbiting scroll member can be held with high accuracy, the tooth tip bottom gap can be properly held, and energy efficiency can be improved.
[0066]
Further, since the distribution force is given using the gas of the discharge pressure, as described in the above embodiment, the area of the non-swirl attracting pressure region can be reduced, the non-swivel end plate can be reduced in diameter, and the compressor can be reduced in diameter. There is an effect that can be done.
[0067]
Further, since the end plate space 2f is maintained at the discharge pressure, as described in the above embodiment, the non-revolving end plate is finally deformed (that is, due to the force applied to the side surface of the scroll wrap shown in FIG. 10 and thermal expansion). The deformation added to FIG. 5 is extremely small, and the tooth bottom gap can be extremely small during a wide range of operation, and the energy efficiency is greatly improved by suppressing leakage.
[0068]
Further, since only one pressure equalizing hole 2i is provided, there is almost no gas flow inside the rear outer peripheral groove 2j during steady or near-steady operation. For this reason, there is no fluctuation of the attraction force due to the fluctuation of the flow of the discharge gas, the attraction force is stable, and the non-orbiting scroll member 2 does not vibrate and leakage is suppressed, so that the energy efficiency can be further improved. There is.
[0069]
In addition, since the heat flux flowing into the suction chamber 35 below the rear outer peripheral groove 2j is reduced and the suction heating can be suppressed, the compression power is reduced and the energy efficiency is improved.
[0070]
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.
[0071]
Further, since the non-swirl back chamber 32 becomes the 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 in any part of the case, which has a specific effect that the manufacturability is improved.
[0072]
Further, a hinge type check valve 24 is provided at the outlet of the discharge hole 2d, and the tip of the valve plate is in contact with the gas inlet of the discharge pipe 25. When the compressor is stopped, the gas tries to flow backward from the discharge pipe 25 to the inner space 2f of the end plate. However, due to the flow, the tip of the check valve 24 is pushed to instantly close the discharge hole 2d, and the gas flows backward. prevent. Since the structure is simple and the posture at the time of opening and closing is stable, there is a specific effect that the opening / closing operation is stable and a highly reliable check valve can be realized. The check valve 24 may be magnetized. In this case, when the check valve is open during operation, the valve is attached to the discharge cover 2c, so that the check valve does not cause any unstable operation, the discharge flow path resistance is reduced, and energy efficiency is further improved. There is a unique effect of improving.
[0073]
Further, since the discharge pipe 25 is connected to the discharge cover 2c on the side surface, the rigidity of the discharge pipe 25 in the axial direction is reduced. As a result, when the non-orbiting scroll member 2 moves in the axial direction, the non-orbiting release action can be reliably performed without being obstructed, and the inside of the compression chamber 33 due to liquid compression or an accident is extremely excessive. When the pressure is generated, the pressure can be instantaneously reduced, and there is a specific effect that the compression chamber forming portion such as the scroll member is prevented from being broken and the reliability is improved. This also has a specific effect that the height of the non-turning back chamber 32 is reduced and can be reduced in size.
[0074]
Further, a conformable coating 3 i is provided on the front surface side of the scroll wrap 3 b and the orbiting end plate 3 a of the orbiting scroll member 3. As a result, it becomes possible to avoid an increase in the gap due to an error in the component dimensions that determines the tooth tip bottom gap, so that the energy efficiency can be further improved.
[0075]
Next, the flow of oil will be described.
[0076]
The oil in the oil storage chamber 27 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 small amount of oil is supplied to the shaft thrust surface 9e through the gap between the upper surface of the inner rotor 26a and the circular dig 9f. The oil is supplied to the spherical bearing portion 9g on the outer periphery of the floating bearing bush 9a and goes out to the lower portion of the motor chamber 30. Thereafter, the oil returns to the oil storage chamber 27 from the oil hole 18 a in the outer peripheral portion of the auxiliary bearing oil supply support plate 18.
[0077]
Part of the oil that has entered the shaft oil supply hole 8a first enters the sub-bearing oil supply hole 8c, and supplies the cylindrical bearing between the shaft 8 and the floating bearing bush 9a. Thereafter, the oil enters the motor chamber 30 via the spherical bearing portion 9g or directly returns to the oil storage chamber 27 through the oil hole 18a.
[0078]
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 an oil supply spiral groove 8i, and the amount of oil supplied to the main bearing 4d is determined by this 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 swivel bearing 8f.
[0079]
The supplied oil flows into the swivel back space 34. Since the back pressure valve 10 is provided, the pressure in the orbiting back space 34 is higher than the suction pressure that is the pressure on the outlet side of the oil discharge passage 4f by a value corresponding to the amount of compression of the valve spring 10b.
[0080]
Here, part of the oil flows into the frame oil groove 4c of the thrust bearing 4a and the swirl oil groove 3c of the thrust surface 4d, and finally flows into the suction chamber 35 while supplying oil to the thrust surface. Then, the inside of the compression chamber 33 is sealed.
[0081]
Most of the other oil flows to the vicinity of the inner wall of the cylindrical case 21 through the oil discharge passage 4f, and then finally flows into the oil storage chamber 27 through the mounting outer peripheral groove 11a and the stator outer peripheral groove 16a of the mounting member 11. . In addition, you may provide a groove | channel in the cylindrical case 21 instead of the stator outer periphery groove | channel 16a from which this oil flows down. For example, it is good also as a seam when a cylindrical case is created from a board. The reason is that a small groove is generally formed on the inner peripheral side.
[0082]
Further, since the pressure in the orbiting back space 34 becomes higher than the suction pressure, an attractive force of the orbiting scroll member 3 is generated thereby. 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 as a thrust surface, and can reduce the urging force applied thereto, that is, the thrust bearing load. For this reason, the sliding loss in the location can be reduced and there exists a characteristic effect that energy efficiency improves. 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.
[0083]
Next, a sixth embodiment of the present invention will be described with reference to FIG. FIG. 7 is a plan view showing a discharge pipe portion of a scroll compressor according to a sixth embodiment of the present invention.
[0084]
In the sixth embodiment, the connection portion of the discharge pipe 25 to the case is brought to the central portion in the fifth embodiment. By doing so, the spring force of the discharge pipe acts parallel to the non-orbiting scroll member 2 at the center axis position when the non-orbiting scroll member 2 moves upward. There is a peculiar effect that the vertical movement of the non-orbiting scroll member can be smoothly performed and the reliability can be improved. Further, when the discharge pipe 25 is fixed to the case, the vertical portion 25a may be pushed and fixed to the inside of the case from the neutral position so that an attractive force is generated in the non-orbiting scroll member 2. In this case, it is possible to generate an attracting force even during the start-up in which no attracting force is generated by the non-swing attracting pressure region 29, and it is possible to perform the start-up smoothly. The time of the abnormal state that becomes high can be shortened, and there is a specific effect that high reliability can be realized. Further, since the non-swirl attracting pressure region 29 can be reduced, there is a specific effect that the compressor can be reduced in size.
[0085]
Next, a seventh embodiment of the present invention will be described with reference to FIG. FIG. 8 is a longitudinal sectional view of a non-orbiting attraction pressure region portion of the scroll compressor according to the seventh embodiment of the present invention.
[0086]
In the seventh embodiment, the discharge pipe 25 is connected not to the non-orbiting scroll member 2 movable with respect to the case but to the stationary non-orbiting presser 7 in comparison with that of the fifth embodiment. Instead of the pressure hole 2i, the discharge cover 2c is provided with one or a plurality of discharge passages 2k having a large flow passage cross-sectional area and a small flow passage resistance, and two seals 28 are provided in place of the ring seal 22. This eliminates the elasticity required for the discharge pipe in the fifth embodiment, and allows the discharge pipe 25 to have only a vertical portion. For this reason, when the upper case 19 is inserted into the cylindrical case 21, it is not necessary to already attach the discharge pipe. After the upper case 19 is inserted, the discharge pipe 25 can be fixed to the non-rotating presser 7. Become. As a result, there is a specific effect that the assembling property is dramatically improved, and the manufacturing cost can be greatly reduced.
[0087]
In each of the embodiments described above, the non-orbiting scroll member is supported only by the support member separate from the orbiting scroll member. However, the same applies even if the orbiting scroll member is shared as a part of the support member. It has the effect of.
[0088]
【The invention's effect】
According to the present invention, the deformation of the non-orbiting scroll member can be suppressed in a wide operating range, and the gap between the tip of the scroll wrap and the tooth bottom of the orbiting scroll member and the bottom of the orbiting scroll member can be kept small in a wide range. Leakage can be reduced to obtain an energy efficient scroll compressor.
[Brief description of the drawings]
FIG. 1 is an explanatory diagram schematically showing a deformed state during normal operation in which a non-orbiting pulling force is applied on a line to a non-orbiting scroll member of a scroll compressor according to a first embodiment of the present invention. It is.
FIG. 2 is an explanatory diagram schematically showing a deformed state during normal operation in which a non-orbiting attractive force of an intermediate pressure is distributed and applied to a non-orbiting scroll member of a scroll compressor according to a second embodiment of the present invention. FIG.
FIG. 3 schematically shows a deformation state during normal operation in which a non-orbiting attractive force of a discharge pressure is distributed and applied to a non-orbiting scroll member of a scroll compressor according to a third embodiment of the present invention. FIG.
FIG. 4 schematically shows a deformed state during normal operation in which a non-orbiting scroll force of a discharge pressure is distributed and applied to a non-orbiting scroll member having an end plate space of a scroll compressor according to a fourth embodiment of the present invention. It is explanatory drawing shown emphasized.
FIG. 5 is a longitudinal sectional view of a scroll compressor according to a fifth embodiment of the present invention.
6 is a longitudinal sectional view of a different part of the scroll compressor of FIG. 5;
FIG. 7 is a plan view showing a discharge pipe portion of a scroll compressor according to a sixth embodiment of the present invention.
FIG. 8 is a longitudinal sectional view of a non-swirl attracting pressure region portion of a scroll compressor according to a seventh embodiment of the present invention.
FIG. 9 is an explanatory diagram schematically showing a deformed state during normal operation in which discharge pressure is applied to a non-orbiting scroll member of a conventional scroll compressor in a wide area.
FIG. 10 is an explanatory diagram schematically showing a deformed state of a compression chamber of a non-orbiting scroll member of a conventional scroll compressor due to fluid pressure and temperature.
[Explanation of symbols]
2 ... non-turning scroll member, 2a ... non-turning end plate, 2f ... end plate space, 2u ... non-turning reference plane, 3 ... turning scroll member, 3a ... turning end plate, 4 ... frame, 5 ... Oldham ring, 6 ... Non-swivel holder, 8 ... Shaft, 22 ... Ring seal, 26 ... Oil pump, 29 ... Non-swivel attracting pressure region, 33 ... Compression chamber, 34 ... Revolving back space.

Claims (2)

An orbiting scroll member having an end plate and a spiral scroll wrap standing on the end plate,
A non-orbiting scroll member that includes an end plate and a spiral scroll wrap standing on the end plate and is allowed to move in the axial direction;
A compression chamber in which the volume is reduced by substantially closing the scroll member formed by meshing both scroll members;
The non-orbiting pulling force in the direction of attracting the end plate of the non-orbiting scroll member is opposed to the non-orbiting pulling force in the direction of separating the end plate of the non-orbiting scroll member due to the pressure of the fluid on the compression chamber side. A non-orbiting attractive force adding means applied to the orbiting scroll member;
A non-orbiting scroll support member that causes the non-orbiting scroll member to generate a reaction force of a non-orbiting biasing force that is a vector sum of the non-orbiting attraction force and the non-orbiting attraction / separation force;
The non-orbiting scroll member has a suction center in the back center region thereof,
The non-orbiting attraction force adding means provides a non-orbiting attraction force by applying a discharge pressure by providing a non-orbiting attraction pressure area on the outer peripheral portion of the back surface of the non-orbiting scroll member during normal operation. Having the non-orbiting attraction force of a magnitude such that the orbiting biasing force is directed toward the orbiting scroll member;
The non-orbiting support member has at least a part formed separately from the orbiting scroll member, and at least a part of a support surface for the non-orbiting scroll member in the part formed separately from the non-orbiting scroll member is the non-orbiting attractive force. A scroll compressor characterized in that it is formed so as to overlap with the working area. 2. The scroll compressor according to claim 1, wherein the non-orbiting scroll member has an end plate inner space for discharge pressure formed in a central portion of the end plate corresponding to the compression chamber .

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