JP3882785B2 - Scroll compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scroll compressor used in a refrigeration air conditioner, an air compressor, and the like. In particular, the orbiting scroll includes orbiting wraps on both sides of a flat plate, and a drive shaft for moving the orbiting scroll in an eccentric circle includes the orbiting scroll and a stationary device. The present invention relates to a scroll compressor provided to penetrate a scroll.
[0002]
[Prior art]
[Patent Document 1]
JP-A-5-187372
As this type of scroll compressor, for example, as described in Japanese Patent Application Laid-Open No. 5-187372, one orbiting scroll in which a single involute trap is formed on each of both axial surfaces of a flat plate (end plate), A pair of stationary scrolls that form one involute trap that fits into the lap of the scroll, a main shaft for revolving the orbiting scroll through the orbiting scroll and the fixed scroll, and further rotating the orbiting scroll. In order to prevent this, a configuration is disclosed that includes three driven crankshafts and bearings for regulating rotation, which are provided on the outer peripheral side of the lap forming space with positions shifted by 120 ° in the circumferential direction. Also, a concave groove is provided in the wrap end surface facing the mirror surface of the mating scroll, and a self-lubricating sealing member (chip seal) is inserted into the groove, and the wrap end surface and the mating scroll are interposed via the chip seal. A configuration for sliding contact is disclosed.
[0003]
[Problems to be solved by the invention]
In such a conventional scroll compressor, since the main shaft passes through the central portion of the scroll, it is necessary to start winding the spiral wrap from the outside. Since the volume increases as the minimum confinement chamber formed by the wrap consisting of involute or other curves becomes the outer circumference, the specific compression ratio (compression chamber volume at the start of compression and compression chamber volume at the start of discharge) In order to secure the ratio, the number of turns of the wrap must be increased outward, and the outer shape (diameter) of the scroll increases. Further, since the rotation prevention mechanism for preventing the rotation of the orbiting scroll is formed on the outer peripheral edge of the end plate protruding further outward than the winding end of the wrap, the outer shape of the compressor is further increased. There's a problem. Accordingly, in such a conventional scroll compressor, for example, in a scroll compressor for refrigeration and air conditioning, a small form in which the required rated power of the scroll compressor is 5 horsepower class and the outer shape (diameter) of the compressor is 160 mm or less. Could not be configured.
[0004]
And since the end plate itself on the orbiting scroll side is formed relatively thick, there is a problem that the weight of the entire orbiting scroll increases, the bearing load due to the centrifugal force accompanying the eccentric rotation increases, and the vibration also increases. . In addition, since the wrap end surface and the mating scroll are brought into sliding contact with each other through the tip seal, there is a problem that the efficiency and reliability of the scroll compressor are greatly affected by the wear resistance of the tip seal.
[0005]
An object of the present invention is to provide a scroll compressor that is small in size and has good performance and reliability.
[0006]
Specifically, the outer shape of the orbiting scroll is reduced to a form suitable for high-speed rotation so that a wide range of output control can be realized while maintaining quiet operation.
[0007]
In addition, the gap formed at the tip of the wrap is properly maintained, and stable operation can be maintained by preventing a large force from acting on the orbiting scroll due to liquid compression or abnormal increase in compression chamber pressure. There is to do.
[0008]
[Means for Solving the Problems]
One feature of the present invention is that a orbiting scroll provided with spiral orbiting wraps on both sides of a flat plate, and a stationary lap that is installed on both sides of the orbiting scroll and is combined in an eccentric state so as to face the orbiting wrap. A stationary scroll and a drive shaft that is provided through the orbiting scroll and the stationary scroll and moves the orbiting scroll eccentrically in the stationary scroll, and prevents the orbiting scroll from rotating with respect to the stationary scroll. In a scroll compressor that compresses gas by performing an eccentric circular motion, a concave groove is formed on the outer peripheral surface of the flat plate of the orbiting scroll, and the rotating scroll is prevented from rotating by engaging with the orbiting scroll in the concave groove. However, the Oldham coupling that allows the eccentric circular motion is accommodated and installed.
[0009]
Specifically, the end portion of the outer curve of the orbiting wrap of the orbiting scroll is formed so as to approach or coincide with the outer peripheral edge of the flat plate of the orbiting scroll, and the Oldham joint is divided at the center of the key portion It is characterized by the fact that they are connected in series.
[0010]
The stationary scroll and a frame that supports the stationary scroll so as to be able to advance and retreat are formed by a working chamber that pressurizes the stationary scroll in the direction of the orbiting scroll, and a lap of the working chamber, the orbiting scroll, and the stationary scroll. A communication passage communicating with the compression chamber is provided.
[0011]
Further, the orbiting scroll is divided into two in the axial direction of the drive shaft at the position of the flat plate, and the orbiting scroll is continuously provided with the divided surfaces facing each other.
[0012]
Then, an elastic body is interposed between the split surfaces of the divided orbiting scrolls so as to extend and contract in the axial direction, a concave groove portion is formed in an outer peripheral edge portion of the divided surface, and the orbiting is formed in the concave groove portion. An Oldham coupling that allows the eccentric circular motion while being engaged with the scroll and preventing the rotation of the orbiting scroll is accommodated and installed.
[0013]
Further, the external dimensions of the compressor are configured such that the required rated power is 160 mm or less in a 5-horsepower class.
[0014]
The structure in which the end portion of the outer curve at the winding end portion of the orbiting wrap is close to or coincides with the outer peripheral edge of the flat plate (end plate) can reduce the end plate outer shape of the orbiting scroll. In addition, the Oldham joint is formed in a ring shape, and is divided into two parts from the center of the key width, and the Oldham joint is accommodated and slid in the recessed groove formed on the outer periphery of the end plate of the orbiting scroll. Thus, the compressor outer shape becomes smaller. Therefore, for example, in a scroll compressor for refrigeration and air conditioning, it is possible to configure the compressor with a required rated power of 5 horsepower class and an outer shape of the compressor of φ160 or less.
[0015]
Furthermore, the configuration in which the stationary scroll and the orbiting scroll are relatively released in the axial direction allows the compressor to be operated while the gap between the orbiting scroll wrap tip and the stationary scroll lap tip is always kept at an appropriate gap. And, for example, when a phenomenon such as liquid compression or abnormal rise in pressure in the compression chamber occurs, the stationary scroll is released from the orbiting scroll, and the side surface of the outer peripheral edge of the orbiting scroll end plate and the outer end of the stationary scroll end plate are removed. An abnormal load on the sliding surface on the side surface of the peripheral edge can be avoided.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
[0017]
FIG. 1 is a longitudinal side view showing a first embodiment of a scroll compressor according to the present invention cut out at an angle of 90 °, FIG. 2 is a perspective view of an Oldham joint used in this embodiment, and FIG. Is a cross-sectional plan view of the orbiting scroll, and FIGS. 4 and 5 are cross-sectional plan views of the identification (fixed) scroll.
[0018]
In FIG. 1, this scroll compressor includes a cylindrical sealed container 1 that is sealed at both ends and arranged with a substantially vertical axis, and an axial center at the upper part of the sealed container 1. The first frame 2 and the second frame 3 that are fixed in alignment with each other, and a spiral stationary wrap is formed on one side, and the stationary frame is aligned with the first frame 2 and the second frame 3 with their axes aligned with each other. A first stationary scroll 4 and a second stationary scroll 5 slidably fitted in the first frame 2 and the second frame 3 so as to face downward and upward, respectively, and spirals on both sides of the flat plate Teeth that are symmetrically formed and are included so that the wraps are opposed to each other so as to be sandwiched between the first stationary scroll 4 and the second stationary scroll 5 and the shaft center is eccentrically movable. Mold turning A crawl 6, a stator 7 a and a rotor 7 b that constitute an electric motor for driving the orbiting scroll disposed below the second frame 3 with the axial center of the first stationary scroll 4 and the second stationary scroll 5 aligned. The first stationary scroll is provided so as to pass through the wall of the hermetic container 1 and the crankshaft 8 that is coupled to the rotor 7b and rotates to cause the orbiting scroll 6 to move eccentrically via the orbiting bearing 6b. 4 is composed of a suction pipe 9 for supplying a compressed gas to a space formed by a stationary wrap 4 and a swirl wrap of the orbiting scroll 6, a discharge pipe 10 disposed through the wall surface of the hermetic container 1, and the like. . The second frame 3 is fixed to the wall surface of the hermetic container 1, and the first frame 2 is connected to the second frame by a through bolt that penetrates the first stationary scroll 4 and the second stationary scroll 5 from the first frame 2. 3 is fixed.
[0019]
A crankshaft 8 as a drive shaft includes a rotor coupling portion 8d coupled to the rotor 7b, and a second frame bearing 3a that extends upward from the rotor coupling portion 8d and is fixed to the center of the second frame 3. A lower support shaft portion 8b supported by the shaft, an eccentric shaft portion 8a extending above the lower support shaft portion 8b and fitted to the swivel bearing 6b, and extending upward from the eccentric shaft portion 8a to the first frame. 2 is formed on an upper support shaft portion 8c supported by a first frame bearing 2a fixed at the center of 2 and an auxiliary frame 11 extending downward from the rotor coupling portion 8d and fixed to the wall surface of the hermetic container 1. The lower end support shaft portion 8e is supported by the auxiliary bearing 12. The crankshaft 8 has a lower balance weight 13 attached to the lower support shaft portion 8b and an upper support shaft portion 8c attached to the upper support shaft portion 8c in order to counteract the centrifugal force of the orbiting scroll 6 and the moment caused by the centrifugal force to prevent the occurrence of vibration. A balance weight 14 is attached. The second frame bearing 3a has a flanged bearing structure and supports the weight of the crankshaft 8 and the rotor 7b.
[0020]
The orbiting scroll 6 is restrained from rotating (rotating around the eccentric shaft portion 8a) by the Oldham coupling 15 and is driven by the rotation of the eccentric shaft portion 8a to perform an eccentric circle (turning) motion.
[0021]
As shown in FIG. 2, the Oldham joint 15 is formed in an oval ring shape by continuously connecting two ring portions 15a and 15b, and has six key portions 15c, 15d, 15e and 15f. , 15g and 15h. The end surfaces in the key width direction of the key portions 15c and 15h and the key portions 15e and 15f form a butting surface connecting the two ring portions 15a and 15b. The key portions 15d and 15g of the Oldham joint 15 are engaged with key grooves 6c and 6d formed in the orbiting scroll 6 shown in FIG. 3, so that the orbiting scroll 6 is relatively moved in the key groove direction. The key portions 15c and 15h and the key portions 15e and 15f are engaged with the key grooves 5b and 5c formed in the second stationary scroll 5 shown in FIG. Relative sliding. Further, the short diameter regions of the ring portions 15a and 15b of the Oldham coupling 15 are relatively slid in the key groove direction in the concave groove portion 6e formed in the axial center portion of the outer peripheral surface of the end plate of the orbiting scroll 6. Thus, the long diameter region is exposed outside the outer peripheral surface of the end plate and engaged with the key grooves 5b and 5c of the second stationary scroll 5 so as to slide in the key groove direction.
[0022]
As shown in FIG. 3, the orbiting scroll 6 has an arcuate start portion (center portion) of the orbiting wrap 6a formed on both sides of the end plate 6f. Is close to or coincides with the outer peripheral edge of the end plate 6f. With this shape, the outer shape of the end plate 6f of the orbiting scroll 6 can be reduced with respect to the number of turns of the orbiting wrap 6a. A discharge passage 6g (6i) and a discharge hole 6h are provided in the outer peripheral portion of the slewing bearing 6a. The discharge passages 6g (6i) are formed on both sides in the axial direction of the orbiting scroll 6 (upper and lower side surfaces in FIG. 1) and communicate with each other through the discharge holes 6h.
[0023]
As shown in FIG. 4, in the second stationary scroll 5, the winding start portion (inner peripheral end portion) and winding end portion (outer peripheral end portion) of the stationary wrap 5 a are both formed by arcs, and the winding of the stationary wrap 5 a is performed. The fitting hole 5d is provided in the vicinity of the inside of the start portion. On the other hand, a suction passage 5e is provided in the vicinity of the inside of the winding start portion of the stationary wrap 5a.
[0024]
As shown in FIG. 5, the first stationary scroll 4 communicates with a suction pipe 9 installed through the wall surface of the sealed container 1 in the vicinity of the winding end portion (outer peripheral end portion) of the stationary wrap 4 a. The suction port 4b is open. On the other hand, in the vicinity of the winding start portion (inner peripheral end portion) of the stationary wrap 4a, an opening is made in the discharge passage 6g formed at both end portions (upper end surface in FIG. 1) in the axial direction of the orbiting scroll 6. A discharge hole 4c is provided. The discharge hole 4c is communicated with a discharge space 1a in the upper part of the closed container 1 by a discharge passage 2c formed in the first frame 2.
[0025]
A section sandwiched between the orbiting wrap 6a of the orbiting scroll 6, the stationary wrap 4a of the first stationary scroll 4 and the stationary wrap 5a of the second stationary scroll 5 forms compression chambers 16 and 17, and the compression chamber 16 The compression chamber 17 communicates with the discharge passage 6g.
[0026]
In the scroll compressor configured as described above, when the orbiting scroll 6 moves eccentrically (orbiting) by the rotational drive of the crankshaft 8, the fluid to be compressed is sucked from the suction pipe 9 and compressed in the compression chambers 16 and 17, and is predetermined. Is discharged from the discharge passage 2a to the discharge space 1a above the sealed container 1 through the discharge passages 6g and 6i, the discharge hole 6h and the discharge hole 4c, and then through the discharge pipe 10 to the sealed container. 1 is discharged outside.
[0027]
Next, the release structure of the first and second stationary scrolls 4 and 5 when the pressure in the compression chambers 16 and 17 becomes abnormally high or the liquid compression phenomenon occurs will be described.
[0028]
The fitting structure of the first stationary scroll 4 with respect to the first frame 2 is such that a ring-shaped concave portion 2b formed on the inner surface of the first frame 2 and a ring-shaped convex portion 4e formed on the outer surface of the first stationary scroll 4 are used. The seal ring 4d is fitted to the slidably fitted in the axial direction, and a ring-shaped working chamber 18 is formed between the bottom of the recess 2b and the tip of the projection 4e. On the other hand, the fitting structure of the second stationary scroll 5 with respect to the second frame 3 is such that the ring-shaped concave portion 5f formed on the inner surface of the second frame 3 has a ring-shaped convex portion formed on the outer surface of the second stationary scroll 5. A seal ring 3b is fitted to the portion 3c so as to be slidable in the axial direction, and a ring-shaped working chamber 19 is formed between the bottom of the recess 5f and the tip of the projection 3c. . The two working chambers 18 and 19 communicate with the compression chambers 16 and 17 through communication holes 4 f and 5 g drilled in the first stationary scroll 4 and the second position scroll 5. Here, the pressure in the working chambers 18 and 19 can be arbitrarily set according to the opening positions of the communication holes 4f and 5g with respect to the compression chambers 16 and 17, and is set to be an intermediate pressure or a suction pressure. .
[0029]
The axial side surface of the outer peripheral edge of the end plate of the second stationary scroll 5 and the contact (butting) surface of the outer peripheral edge of the second frame 3 and the first frame 2 have the same axial dimension within a machining tolerance. Processed and assembled so that When the orbiting scroll 6 is assembled into the second stationary scroll 5 in this state (the end plate of the second stationary scroll 5 and the end plate of the orbiting scroll 6 are in contact), the tip of the wrap 6a of the orbiting scroll 6 and the second An appropriate gap is set at the tip of the wrap 5a of the stationary scroll 5 from the viewpoint of performance and reliability. In other words, an appropriate gap is set from the viewpoint of performance and reliability, and the wrap length of the wrap 6a of the orbiting scroll 6 is determined based on the wrap length of the wrap 5a of the second stationary scroll 5. In the same way, the wrap length of the first stationary scroll 4 and the orbiting scroll 6 is also determined. Here, the reference is that the side surface of the outer peripheral edge of the end plate of the first stationary scroll 4 is in contact with the side surface of the outer peripheral edge of the end plate of the second stationary scroll 5. In this way, the axial dimension is determined based on the side surface of the outer peripheral edge of the end plate of the second stationary scroll 5.
[0030]
Next, the gap between the tip of the wrap 6a of the orbiting scroll 6 and the tip of the wrap 5a of the second stationary scroll 5 when the compressor is operating will be described. In order to simplify the description, the relationship between the orbiting scroll 6 and the second stationary scroll 5 will be described. The axial force acting on the second stationary scroll 5 is as follows: (1) the second stationary scroll 5 is a force that pushes the second stationary scroll 5 upward (the direction in which the second stationary scroll 5 is pressed against the orbiting scroll 6). The force (F1) obtained by multiplying the axial projection area of the space 5h formed by the crankshaft 8 and the wall surface of the ring-shaped recess 5f at the center of the discharge pressure (F1), (2) Force (F2) obtained by multiplying the pressure in the working chamber 19; (3) Force (F3) obtained by multiplying the axial projection area of the space 20 formed by the wall surface of the ring-shaped recess 5f and the second frame by the suction pressure. Works. On the other hand, the compression force (F4) of the compression chamber 17 acts as a force for pushing the second stationary scroll 5 downward (the direction in which the second stationary scroll 5 is to be separated from the orbiting scroll 6). As a result, the second stationary scroll 5 generates a differential moving force in balance between the resultant force F1 to F3 and the compression force F4. Here, if the operating conditions of the compressor are determined, the forces determined are F1, F3, and F4, and the clearance between the tip of the wrap 6a of the orbiting scroll 6 and the tip of the wrap 5a of the second stationary scroll 5 is determined by F2. become. In other words, the force F2, that is, the axial projection area of the working chamber 19 or the pressure in the working chamber 19 is determined so as to have a certain appropriate gap determined from the viewpoint of performance and reliability.
[0031]
Next, the operation will be described. When the scroll compressor configured as described above is operated, the balance of the forces F1 to F4 is normally set to satisfy F1 + F2 + F3 ≧ F4, and the tip of the wrap 6a of the orbiting scroll 6 and the second stationary position are set. The outer peripheral edge of the end plate of the first stationary scroll 4 and the second stationary scroll 5 while maintaining an appropriate (set) gap value between the wrap 5a of the scroll 5 and the tip of the wrap 4a of the first stationary scroll 4 And the side surface of the outer peripheral edge of the end plate of the orbiting scroll 6 are in sliding contact with each other. From this state, for example, when a phenomenon such as liquid compression or abnormal increase in pressure in the compression chamber occurs, the balance of the forces F1 to F4 becomes F1 + F2 + F3 <F4, and the second stationary scroll 5 and the first stationary scroll 4 Is generated from the orbiting scroll 6 and the first and second stationary scrolls 4 and 5 are retreated in the axial direction to the side surface of the outer peripheral edge of the first stationary scroll 4 and the second stationary scroll. When the sliding contact with the orbiting scroll 6 on the side surface of the outer peripheral edge of the end plate 5 is released and the gap at the tip of the wrap is widened, the pressure (high pressure) leaks to the low pressure side, the pressure drops, and the pressure rises abnormally There is no longer to do. Accordingly, the stationary scrolls 4 and 5 and the orbiting scroll 6 do not need to be thick members that can withstand abnormal pressure, and can be made small and lightweight with thin members that can withstand a desired pressure.
[0032]
In this embodiment, both the first stationary scroll 4 and the second stationary scroll 5 are configured to be released in the axial direction. However, the present invention is not limited to this, for example, the first stationary scroll. 4 and the first frame 2 can be used as a single member, which is fixed to another member as the first stationary scroll 4 and can be modified so that only the second stationary scroll 5 is released in the axial direction.
[0033]
As described above, according to this embodiment, the end portion of the outer curve of the winding end portion of the wrap 6a of the orbiting scroll 6 is made close to or coincides with the peripheral edge of the end plate, so that the end plate of the orbiting scroll 6 is The external shape could be reduced.
[0034]
Further, the Oldham joint 15 has a ring-like structure in which a ring portion divided into two from the center of the key width is joined, and the ring portion 15a of the Oldham joint 15 is formed in a recess 6e formed in the center portion in the axial direction of the end plate of the orbiting scroll 6. , 15b are accommodated so as to slide in the recesses 6e, respectively, the outer shape of the compressor can be reduced.
[0035]
Further, the first stationary scroll 4 or the second stationary scroll 5 can be released in the axial direction with respect to the orbiting scroll 6, so that the gap between the wrap tip of the orbiting scroll 6 and the wrap tips of the stationary scrolls 4 and 5 is increased. The compressor can be operated while always maintaining the proper gap, and the stationary scrolls 4 and 5 are released from the orbiting scroll 6 when a phenomenon such as liquid compression or abnormal increase in pressure in the compression chamber occurs. By doing so, it is possible to obtain an effect that it is possible to avoid an abnormal load on the sliding contact surfaces of the side surface of the outer peripheral edge of the end plate of the orbiting scroll 6 and the side surface of the outer peripheral edge of the end plate of the stationary scrolls 4 and 5.
[0036]
Furthermore, when the electric motor that drives the orbiting scroll 6 is rotated at a high speed (for example, 6000 to 9000 rpm) by inverter control in order to perform a wide range of output control with a small compressor, a large centrifugal force is generated by the eccentric rotational motion of the orbiting scroll 6. appear. This centrifugal force is canceled by the lower balance weight 13, but a moment is generated on the crankshaft 8 with the second frame bearing 3 a as a fulcrum. However, since this moment is canceled by the upper balance weight 14 attached to the outer end of the upper support shaft portion 8c, vibration does not increase even in a high-speed rotation state, and a quiet operation can be realized.
[0037]
Next, another embodiment of the present invention will be described. FIG. 6 is a longitudinal sectional side view showing a second embodiment of the scroll compressor according to the present invention, cut out at an angle of 90 ° and developed. FIG. 7 is a perspective view of an Oldham joint used in this embodiment. Here, the same reference numerals are attached to the same components as those in the first embodiment shown in FIGS. 1 to 5, and the detailed description thereof is omitted.
[0038]
The feature of this embodiment is that the orbiting scroll has a two-part structure in the axial direction as compared with the first embodiment. That is, the first turning scroll 60 is provided facing the first stationary scroll 4, and the second turning scroll 61 is provided facing the second stationary scroll 5. The ring portion 15a of the Oldham joint 15 is slidably accommodated in a recess 6e formed in the axially central portion of the first orbiting scroll 60 and the second orbiting scroll 61. It is responsible for preventing rotation. As shown in FIG. 7, the Oldham joint 15 is composed of one ring portion 15a and four key portions 15c, 15d, 15e and 15g, and the first orbiting scroll 60 and the second orbiting scroll. 61, engages with key grooves formed in the first stationary scroll 4 and the second stationary scroll 5 and slides in the grooves.
[0039]
The greatest merit of using the orbiting scroll with both teeth is that the axial thrust loads generated when compressing the fluid to be compressed are canceled each other, and the deformation of the orbiting scroll end plate due to the compressive load is avoided. In a single-tooth orbiting scroll, the orbiting scroll end plate must be thickened to prevent deformation of the orbiting scroll end plate, but if the orbiting scroll is configured as in this embodiment, the upper and lower orbiting scrolls 60 and 61 are deformed. Since they are regulated, the end plates of the orbiting scrolls 60 and 61 can be made as thin as possible.
[0040]
Since the release structure and operation of the fixed scrolls 4 and 5 are the same as those in the above-described embodiment, the description thereof is omitted.
[0041]
As described above, according to this embodiment, since the orbiting scrolls 60 and 61 are divided into two in the axial direction, the Oldham joint 15 can be integrally configured to be downsized and the assemblability is improved. Furthermore, there is an effect that the thickness of the end plates of the orbiting scrolls 60 and 61 can be reduced.
[0042]
Next, still another embodiment of the present invention will be described. FIG. 8 is a longitudinal sectional side view showing a third embodiment of the scroll compressor according to the present invention, which is cut out at an angle of 90 ° and developed. Here, the same reference numerals are given to the components common to the first embodiment and the second embodiment, and the description of the structure of the portion is omitted.
[0043]
The feature of this embodiment is that elastic support bodies 22 and 23 having a rectangular cross section are interposed between the first orbiting scroll 60 and the second orbiting scroll 61 divided into two parts, and the first orbiting scroll 60 and the second orbiting scroll. The reason is that an appropriate gap is formed on the back surface of the scroll 61 (the side opposite to the wrap). The elastic supports 22 and 23 are formed of a self-lubricating member having elasticity and are fitted in ring-shaped grooves formed in the first orbiting scroll 60 and the second orbiting scroll 61. Is done. Since the first orbiting scroll 60 and the second orbiting scroll 61 do not have a relative rotational movement, the elastic supports 22 and 23 do not necessarily need to be self-lubricating members.
[0044]
In the scroll compressor of the single tooth type as well as the double tooth type of this embodiment, the setting of the gap between the wrap tips is the most important factor from the viewpoint of performance and reliability. In other words, how highly efficient the compressor is can be determined by how small the gap between the wrap tips can be set without impairing reliability (durability) during compressor operation. The above-mentioned release structure of the stationary scrolls 4 and 5 can cope with this technical problem, but this embodiment is realized by configuring it so that the orbiting scroll can be released from the stationary scroll. Is.
[0045]
Since the elastic supports 22 and 23 are formed of a self-lubricating member having elasticity, the first and second orbiting scrolls 60 and 61 are to be separated from the first and twelfth stationary scrolls 4 and 5. When a force is generated, a force for contracting the elastic supports 22 and 23 acts on the back surfaces (opposite side surfaces of the wrap) of the first and second orbiting scrolls 60 and 61, and the elastic supports 22 and 23. As a result, the first and second orbiting scrolls 60 and 61 are released from the first and second stationary scrolls 4 and 5 in the axial direction. When the force for separating the first and second orbiting scrolls 60, 61 from the first and second stationary scrolls 4, 5 decreases and the elastic force of the elastic supports 22, 23 increases, A restoring force that presses the second orbiting scrolls 60 and 61 toward the first and second stationary scrolls 4 and 5 is generated. As described above, by installing the elastic supports 22 and 23 between the back surfaces of the first and second orbiting scrolls 60 and 61, the postures of the first and second orbiting scrolls 60 and 61 during the orbiting motion are further stabilized. It becomes possible. Note that the release operation of the first and second stationary scrolls 4 and 5 is the same as described above, and a description thereof will be omitted.
[0046]
According to this embodiment, by installing the elastic supports 22 and 23 between the back of the first orbiting scroll 60 and the second orbiting scroll 61 having a structure in which the orbiting scroll is divided into two axially at the center of the end plate, The postures of the orbiting scrolls 60 and 61 during the orbiting motion can be further stabilized, and the outer peripheral edges of the end plates of the orbiting scrolls 60 and 61 are released by releasing the orbiting scrolls 60 and 61 from the stationary scrolls 4 and 5. There is an effect that it is possible to avoid an abnormal load on the sliding contact surface of the side surface of the end portion and the side surface of the outer peripheral edge of the end plate of the stationary scrolls 4 and 5.
[0047]
When the orbiting scrolls 60 and 61 are moved forward and backward in the axial direction and released from the stationary scrolls 4 and 5, the stationary scrolls 4 and 5 may be fixed to the frames 2 and 3 so that they cannot be moved forward and backward. Similar effects can be obtained.
[0048]
【The invention's effect】
According to the present invention, the Oldham coupling that engages with the orbiting scroll and prevents the rotation of the orbiting scroll while allowing an eccentric circular motion is accommodated in the concave groove formed on the outer peripheral surface of the orbiting scroll. The outer shape of the orbiting scroll can be reduced.
[0049]
Further, by forming the end portion of the outer curve of the orbiting wrap of the orbiting scroll so as to be close to or coincide with the outer peripheral edge of the flat plate of the orbiting scroll, the number of turns of the orbiting wrap is increased with respect to the small-diameter orbiting scroll. And desired compression characteristics can be obtained.
[0050]
In addition, the stationary scroll and the orbiting scroll are relatively moved forward and backward (released) in the axial direction, so that the orbiting scroll is held at the proper gap between the orbiting scroll and the stationary scroll. Since the compressor can be operated while stabilizing the attitude of the compressor, the performance of the compressor can be improved. In addition, when a phenomenon such as liquid compression or abnormal increase in pressure in the compression chamber occurs, the stationary scroll or orbiting scroll is released, causing abnormal load on the sliding contact surface on the outer peripheral edge of the end plate of the scroll. Since it can be avoided, reliability is improved.
[0051]
Furthermore, the balance weight with respect to the eccentric circular motion of the orbiting scroll and the balance weight with respect to the moment acting on the drive shaft are attached to the drive shaft, thereby canceling the centrifugal force and the moment generated by the eccentric circular motion of the orbiting scroll. It is possible to operate quietly while suppressing vibration even at high speed rotation.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view showing a first embodiment of a scroll compressor according to the present invention.
FIG. 2 is a perspective view of an Oldham coupling in the first embodiment shown in FIG. 1;
3 is a cross-sectional plan view of the orbiting scroll in the first embodiment shown in FIG. 1. FIG.
4 is a cross-sectional plan view of a second stationary scroll in the first embodiment shown in FIG. 1. FIG.
FIG. 5 is a cross-sectional plan view of the first stationary scroll in the first embodiment shown in FIG. 1;
FIG. 6 is a longitudinal side view showing a second embodiment of the scroll compressor according to the present invention.
FIG. 7 is a perspective view of an Oldham joint in the second embodiment shown in FIG. 2;
FIG. 8 is a longitudinal side view of a scroll compressor showing a third embodiment according to the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Airtight container, 2 ... 1st frame, 3 ... 2nd frame, 3b ... Seal ring, 4 ... 1st stationary scroll, 4a ... Stationary wrap, 4d ... Seal ring, 4f ... Communication hole, 5 ... 2nd stationary scroll 5a ... Stationary lap, 5g ... Communication hole, 6 ... Orbiting scroll, 6a ... Orbiting lap, 6e ... Groove, 6f ... End plate, 8 ... Crankshaft, 13 ... Lower balance weight, 14 ... Upper balance weight, 15 ... Oldham Joint, 16, 17 ... compression chamber, 18, 19 ... working chamber, 23, 24 ... elastic support.

Claims (5)

A turning scroll provided with spiral orbiting wraps on both sides of a flat plate, a stationary scroll provided on both sides of the orbiting scroll and provided with a stationary wrap that is eccentrically combined to face the orbiting wrap, and the orbiting scroll And a drive shaft for penetrating the orbiting scroll in an eccentric circle within the stationary scroll, and compressing the gas by causing the orbiting scroll to eccentrically move with respect to the stationary scroll while preventing rotation. In the scroll compressor that
A concave groove is formed in the outer peripheral surface of the flat plate of the orbiting scroll, and an Oldham coupling that allows eccentric circular movement while being engaged with the orbiting scroll and preventing the rotation of the orbiting scroll is accommodated in the concave groove. A scroll compressor characterized by that.   2. The balance weight for the eccentric circular motion of the orbiting scroll is attached to the outside of one stationary scroll on the drive shaft, and the balance weight for the moment acting on the drive shaft is attached to the outside of the other stationary scroll. A scroll compressor characterized by that.   The scroll compressor according to claim 1 or 2, wherein an end portion of an outer curve of the orbiting wrap of the orbiting scroll is formed so as to be close to or coincide with the outer peripheral edge of the flat plate of the orbiting scroll.   The scroll compressor according to claim 1, wherein the Oldham coupling is divided and continuously provided at a central portion of the key portion. 5. The scroll compressor according to claim 1 , wherein the stationary scroll is supported so as to advance and retreat in the axial direction of the drive shaft.

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