JP3662757B2 - Scroll compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scroll compressor mainly used for air conditioning and refrigeration equipment.
[0002]
[Prior art]
As this type of electric compressor, there are a compressor having a reciprocating type, a rotary type, and a scroll type. Among them, scroll compressors have been widely put into practical use by taking advantage of high efficiency, low noise, and low vibration.
[0003]
As the basic structure is well known, the fixed scroll with the spiral blades rising on the end plate and the orbiting scroll with the same spiral blades rising on the end plate are meshed, A plurality of compression chambers are formed. When the orbiting scroll is circularly orbited with respect to the fixed scroll without rotating by the circular orbital motion of the eccentric part of the crankshaft, the compression chamber sucks refrigerant in the opening part on the outer peripheral side of the end plate, and then moves to the center side of the end plate. It closes while moving and gradually reduces the volume to compress the refrigerant and finally discharge it.
[0004]
As a rotation preventing mechanism for causing the orbiting scroll to move in a circular orbit without rotating in this way, Japanese Patent Application Laid-Open No. 53-35840 and Japanese Patent Publication No. 07-39832 are shown in FIGS. 22 (a) and 22 (b). A so-called Oldham ring a is used. The Oldham ring a is provided with keys b1 and b2 which are orthogonal to each other on the diameter line between the one surface and the other surface, and the key b1 on the one surface side is fitted into the key groove d1 on the diameter line on the back surface of the orbiting scroll c. The key b2 on the surface side is fitted in the key groove d2 on the diameter line of the bearing member f that supports the crankshaft e at the back of the orbiting scroll c.
[0005]
When the crankshaft e is driven to rotate around the center of rotation supported by the bearing member f, the degree of eccentricity of the bearing h from the eccentric bearing h to the axis i of the orbiting scroll c that fits into the eccentric shaft h. The circular orbital motion with a diameter corresponding to is transmitted. At this time, the orbiting scroll c moves with the Oldham ring a in the first direction in which the movement is restricted by the fitting of the key b2 and the key groove d2, and the fitting of the key b1 and the key groove d1. The single movement in the second direction orthogonal to the first direction regulated by the above-described movement can be prevented, and the rotation in the second direction is prevented, while the movement in the first and second directions is combined to follow the circular orbital motion. Then, the same circular orbital motion is performed and continuous turning drive is received, and the refrigerant is sucked, compressed and discharged with the fixed scroll g.
[0006]
On the other hand, as disclosed in Japanese Patent Laid-Open No. 57-148087, as shown in FIG. 23, a plurality of balls j are sandwiched between a movable ring k on the orbiting scroll side and a fixed ring l on the bearing member side to prevent rotation of the orbiting scroll. A ball coupling system having a mechanism is disclosed. Further, as shown in FIG. 24, Japanese Patent Laid-Open No. 55-46081 discloses a mechanism for preventing rotation of the orbiting scroll c by sandwiching a plurality of pin-like elements m between the orbiting scroll c and the fixing ring l on the bearing member side. A pin-ring type device is disclosed.
[0007]
By the way, compressors used for refrigeration and air conditioning have recently been driven by inverters, and recently, a wide operating range exceeding several Hz to hundreds of tens of Hz corresponding to the state of the moment. It has come to be used in.
[0008]
In such a use situation, when the scroll compressor reaches an operation frequency after the intermediate capacity operation (about 30 Hz) region, the orbiting scroll c is in a normal posture with respect to the fixed scroll g as shown in FIG. Therefore, a so-called rollover phenomenon that tilts by a small angle θ tends to occur. If there is such a rollover, a loss due to refrigerant leakage from between the sliding surfaces between the orbiting scroll c and the fixed scroll g occurs, which is a main factor in reducing the compression efficiency.
[0009]
Conventionally, in order to cope with such a problem, as shown in FIG. 22, a small-sized rollover prevention plate n that does not interfere with the Oldham ring a, that is, fits inside thereof, is provided on the bearing member f, and the back surface of the orbiting scroll c is provided. I try to back it up.
[0010]
[Problems to be solved by the invention]
However, in the Oldham ring type scroll compressor as described above, the Oldham ring itself has a complicated shape, and there are many parts that require high part accuracy such as the size, shape, and positional relationship of the four keys. There are problems in terms of workability and cost. In addition, the ball coupling type and pin / ring type scroll compressors have a large number of parts and assembly man-hours, and also have problems in workability, low cost, and ease of assembly in order to satisfy high accuracy.
[0011]
Further, in the Oldham ring type scroll compressor, the roll-up prevention plate n of the orbiting scroll c is enlarged to a diameter close to the outer diameter of the end plate of the orbiting scroll c. It is easy, but because it is obstructed by the existence of the Oldham ring and is limited to be smaller than its inner diameter, the current situation does not prevent overturning.
[0012]
An object of the present invention is to provide a highly efficient scroll compressor having a rotation prevention mechanism that is excellent in workability, assembly performance, and cost by combining simple shaped parts.
[0013]
[Means for Solving the Problems]
The scroll compressor according to the present invention is formed by meshing a fixed scroll having a spiral blade having substantially the same shape on one surface of a mirror plate and a turning scroll to form a compression chamber therebetween, and the turning scroll is made eccentric to the crankshaft. The circular orbital motion of the part causes the fixed scroll to make a circular orbital motion without rotating through the antirotation mechanism, and the fluid is repeatedly sucked, compressed, and discharged.
[0014]
In order to achieve the above object, in particular, the anti-rotation mechanism exceeds the maximum turning diameter of the circular orbital motion of the orbiting scroll in the first direction substantially orthogonal to the axial direction of the crankshaft. The sliding member penetrated so as to be able to slide relative to each other with a length, and a fixed member around the orbiting scroll. A guide surface that contacts and guides the sliding member in a second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction so that the sliding member can slide within a range exceeding the maximum turning stroke of the orbiting scroll; The main feature is that it consists of
[0015]
In such a configuration, the sliding member and the orbiting scroll have a range equal to or larger than the maximum orbiting stroke of the orbiting scroll in the penetrating direction which is a first direction substantially perpendicular to the axial direction of the crankshaft according to the penetrating structure of the sliding member. The sliding member itself is guided by the guide surfaces of the fixed members around the orbiting scroll at the protruding end surfaces of both ends protruding beyond the maximum orbiting diameter of the orbiting scroll. The orbiting scroll can slide with the orbiting scroll in a second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction, exceeding the maximum orbiting diameter, and the orbiting scroll prevents rotation by such a two-way guide. When the circular orbital motion of the eccentric portion is given from the crankshaft, the sliding in the first direction with respect to the sliding member and the sliding in the second direction with the sliding member The formation, inhalation of the refrigerant between said been subjected to the same circle locomotion and the eccentric portion is pivoted driven continuously fixed scroll, repeated compression and ejection.
[0016]
In particular, the guide surface of the fixed member that passes through the end plate of the orbiting scroll so that the sliding member can slide relative to the orbiting scroll in the first direction, and both ends of the sliding member are provided around the orbiting scroll. Thus, the simple configuration is such that it is guided only in the second direction substantially perpendicular to the first direction, so that a highly efficient scroll compressor can be obtained with good workability and easily ensuring the required accuracy. The attachment and cost are also excellent.
[0017]
In the scroll compressor of the present invention, the rotation preventing mechanism has a maximum turning of the circular orbit motion of the orbiting scroll in the first direction substantially orthogonal to the axial direction of the crankshaft through the groove on the back surface of the end plate of the orbiting scroll. A sliding member that is traversed so as to be relatively slidable with a length that exceeds the diameter, and a fixed member around the orbiting scroll, and protrudes on both sides of the orbiting scroll above the orbiting diameter of the sliding member. The sliding member slides in the second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction within a range equal to or greater than the maximum orbiting stroke of the orbiting scroll. Another feature is that it is composed of a guide surface that guides it to move.
[0018]
In such a configuration, the sliding member and the orbiting scroll are in the first direction substantially perpendicular to the axial direction of the orbiting scroll and the crankshaft according to the transverse structure through the groove on the back surface of the orbiting scroll of the sliding member. As in the case of the above one feature, the sliding member can move relative to the fixed member around the orbiting scroll and the axial direction of the crankshaft and Since the sliding member can move with the orbiting scroll in a second direction substantially orthogonal to both of the first directions, the first or the first sliding member with respect to the sliding member is given when the circular orbital motion of the eccentric portion is given from the crankshaft. And the sliding in the second direction with the sliding member, the same circular movement is performed, and the refrigerant is sucked into and out of the stationary scroll continuously driven by turning. Contraction, repeatedly performed discharge. In particular, the relative sliding between the sliding member and the orbiting scroll is due to the fit with the groove, and the workability and assemblability are better than in the case of penetration, than in the case of the main feature, Workability, cost reduction, and assembly are further improved.
[0019]
In these cases, the sliding member may be one or a plurality of members, and is not particularly limited. When the plurality of sliding members are connected to each other at the same protruding side at both ends, the sliding members depend on the sliding member. The guide rigidity of the orbiting scroll is improved, and the scroll compressor can be made more efficient. Further, if the connecting portion forms a sliding surface with the guide surface, the guided area at both ends of the sliding member by the guide surface increases, so that the guide rigidity here is also improved, and the scroll compressor Further increase in efficiency can be achieved.
[0020]
In the scroll compressor according to the present invention, the rotation prevention mechanism further includes a maximum orbital motion of the orbiting scroll in two directions parallel to the outer periphery of the end plate of the orbiting scroll and a first direction substantially orthogonal to the axial direction of the crankshaft. A frame-shaped sliding member fitted so as to be able to slide relative to each other with a length exceeding the turning diameter, and a fixed member around the turning scroll, which exceeds the turning diameter of the sliding member The sliding member is in contact with the projecting side end surfaces projecting on both sides of the orbiting scroll, and the sliding member is the maximum orbit of the orbiting scroll in the second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction. Another feature is that it is composed of a guide surface that guides it so as to slide within a stroke or more.
[0021]
In such a configuration, the sliding member and the orbiting scroll are substantially perpendicular to the axial direction of the orbiting scroll and the crankshaft according to the fitting structure of the frame-shaped sliding member and the two parallel surfaces of the outer periphery of the orbiting scroll. As in the case of the main feature described above, the sliding member is in the axial direction of the crankshaft between the fixed member around the orbiting scroll and the relative movement in the first direction within the range exceeding the maximum orbiting stroke of the orbiting scroll. Since the sliding member can move with the orbiting scroll in the second direction substantially perpendicular to the first direction, when the circular orbital motion of the eccentric portion is given from the crankshaft, the first relative to the sliding member And the sliding in the second direction with the sliding member, the same circular movement is performed, and the refrigerant is sucked into and out of the stationary scroll continuously driven by turning. Compression, discharge Repeated. In particular, the sliding member has a relative sliding movement with the orbiting scroll due to the fitting with the outer peripheral two surfaces, and the workability and assemblability are further improved compared to the case of the penetration, and the main characteristics of the sliding member are as follows. Compared to the case, the workability, the low cost, and the assemblability are further improved.
[0022]
In each of the above cases, if a fixed member positioned with the orbiting scroll between the fixed scroll and the fixed scroll is provided with a position holding portion that abuts the back surface of the orbiting scroll and holds the orbiting scroll in a close contact position with the fixed scroll. Backing up the outer periphery of the orbiting scroll without any other obstacles, keeping it in close contact with the fixed scroll, making it easier to prevent rollover than before, and maintaining high efficiency of the scroll compressor Become.
[0023]
In addition, if a position holding portion that holds the orbiting scroll at a close contact position with the fixed scroll is provided on the fixed member that is located between the fixed scroll and the orbiting scroll, the orbiting scroll of the sliding member is provided. The supporting force for preventing rollover can be applied to the part farther from the center part of the orbiting scroll, that is, the outer diameter position of the orbiting scroll, by holding the position using both ends protruding from the orbiting scroll. Can be more reliably prevented.
[0024]
Further, when the guide surfaces are in contact with both end portions of the sliding member and the contact surfaces are tapered surfaces or rounded surfaces that gradually approach the fixed scroll side toward the outer diameter side, the orbiting scroll is driven and the circle is driven. Each time the sliding member receives frictional resistance toward each end side by the orbital motion, it receives the guide of the tapered surface or the rounded surface and is pressed to the fixed scroll side to further enhance the degree of adhesion of the orbiting scroll to the fixed scroll. Further, the efficiency of the scroll compressor can be further increased.
[0025]
Further objects and features of the present invention will become apparent from the following detailed description and drawings. Each feature of the present invention can be used alone or in combination in various combinations as much as possible.
[0026]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, several embodiments of the present invention will be described with reference to FIGS.
[0027]
(Embodiment 1)
The first embodiment is an example of a hermetic scroll compressor installed sideways for refrigeration and air conditioning. However, the present invention is not limited to this, and of course does not ask whether the installation direction or the sealed type or not, orbiting scroll so that the orbiting scroll is orbitally moved by the crankshaft via the rotation prevention mechanism In addition, the present invention is applicable to all types in which the refrigerant is repeatedly sucked, compressed, and discharged from the fixed scroll.
[0028]
As shown in FIG. 1, the scroll compressor according to the present embodiment is provided with a compression mechanism 2 that sucks, compresses and discharges refrigerant at one end inside the sealed container 1. The stator 4 of the electric motor 3 that drives the compression mechanism 2 is positioned at the center of the hermetic container 1 and is fixed to the inner surface of the side peripheral wall of the hermetic container 1, and the rotor 5 corresponding to the stator 4 of the electric motor 3 Is connected to a crankshaft 6 which is a drive shaft of the compression mechanism 2, and is arranged so that the axial direction thereof is substantially horizontal. The crankshaft 6 is supported by a main bearing member 10 fixed to the compression mechanism 2 by welding or the like with a main shaft 6a at one end on the compression mechanism 2 side, and a sub shaft 6b at the end opposite to the main shaft 6a. It is supported by a secondary bearing member 11 located on the other end side of the sealed container 1 and fixed to the inner surface of the side wall of the sealed container 1 by welding or the like. The fixed scroll 20 is fixed to the main bearing member 10 by bolts 23, and the orbiting scroll 30 is sandwiched between the two and the orbiting scroll 30 is held so as to be in close contact with the fixed scroll 20.
[0029]
Main and auxiliary bearings 9 and 12 are provided at a portion for supporting the main shaft 6 a of the main bearing member 10 and a portion for supporting the auxiliary shaft 6 b of the auxiliary bearing member 11. The main bearing 9 and the sub-bearing 12 support the rotation of the crankshaft 6, but also support the force due to the gas pressure generated in the crankshaft 6 when the compression mechanism 2 compresses the refrigerant by this rotational movement.
[0030]
The lower part in the airtight container 1 is a lubricating oil reservoir 7, and a suction port 17a of a lubricating oil pump 17 driven at the end of the crankshaft 6 on the side of the countershaft 6b opens into the lubricating oil reservoir 7 for suction. The lubricating oil thus supplied is supplied to sliding portions including the bearing portion of the compression mechanism 2 through a lubricating hole 6c formed so as to pass through from the end of the crankshaft 6 on the side of the auxiliary shaft 6b to the portion of the main shaft 6a.
[0031]
As shown in FIGS. 1 and 2, the compression mechanism 2 includes a fixed scroll 20 in which spiral blades 21 rise on the end plate 22, and a turning scroll 30 in which substantially the same spiral blades 31 rise on the end plate 32. And a plurality of compression chambers 41 are formed therebetween, and the orbiting scroll 30 is caused to move in a circular orbit with respect to the fixed scroll 20 without rotating by the eccentric portion 26 of the crankshaft 6 via the rotation preventing mechanism 42. Repeatedly turn.
[0032]
The rotation prevention mechanism 42 of the first embodiment is shown in FIGS. As shown in these figures, the end plate 32 of the orbiting scroll 30 exceeds the maximum orbiting radius R shown in FIG. 3 in the circular orbital motion of the orbiting scroll 30 in a first direction X substantially perpendicular to the axial direction of the crankshaft 6. Continuous through by penetrating through the through hole 25 (the embodiment shown in FIGS. 1 to 8) or traversing through the groove 34 (the embodiment shown in FIGS. 9 to 17) so that they can slide relative to each other. Are provided on the main bearing member 10 which is one of the fixed members around the orbiting scroll 30, and exceeds the orbiting diameter R of the sliding member 24 on both sides of the end plate. The maximum orbiting stroke S of the orbiting scroll 30 in the second direction Y (FIG. 3) is in contact with the projecting side end surfaces of both ends projecting from each other and substantially perpendicular to both the axial direction of the crankshaft 6 and the first direction. ) Slide in the above range It is composed of a guide surface 27 for sea urchin assistance.
[0033]
In this way, the sliding member 24 and the orbiting scroll 30 are in the first direction X that is substantially perpendicular to the axial direction of the crankshaft 6 according to the longitudinal engagement by the penetrating structure or the transverse structure of the sliding member 24. Alternatively, the sliding member 24 itself can slide relative to the longitudinal engagement direction by traversing within the range of the maximum turning stroke S of the orbiting scroll 30, and the sliding member 24 itself protrudes beyond its maximum turning diameter R from the orbiting scroll 30. The projecting side end surface 24b of the portion 24a is guided by the guide surface 27 of the main bearing member 10 which is one of the fixing members around the orbiting scroll 30, so that both the axial direction of the crankshaft 6 and the first direction X are included. The orbiting scroll 30 is slidable in the second direction Y substantially orthogonal to the rotation direction of the crankshaft 6 while the orbiting scroll 30 is prevented from rotating by such a two-way guide. When the circular orbital motion of the core portion 26 is given, the sliding member 24 slides in the first direction X and the sliding in the second direction Y accompanied by the sliding member 24, thereby combining The same circular movement as that of the eccentric part 26 is performed and continuously driven to rotate, and the refrigerant is repeatedly sucked, compressed, and discharged with the fixed scroll 20.
[0034]
Thus, in order to prevent the orbiting scroll 30 from rotating and to be driven to rotate, the orbiting scroll 30 is moved through the through hole 25 so that the sliding member 24 can slide relative to the orbiting scroll 30 in the first direction. Through longitudinal engagement such as passing through or traversing the groove 34, both end portions 24a of the sliding member 24 are substantially orthogonal to the first direction at the guide surfaces 27 of the main bearing member 10 provided around the orbiting scroll 30. It can be achieved with a simple configuration that only guides in the second direction, has high workability, easily secures the required accuracy, and obtains a highly efficient scroll compressor with excellent assembly and cost. It becomes.
[0035]
In particular, the relative sliding between the sliding member 24 and the orbiting scroll 30 is due to the engagement with the groove 34 of the embodiment shown in FIGS. Since the workability and the assembling property are further improved than in the case of the fitting structure with the example through-hole 25, the workability, the cost reduction, and the assembling property are further improved as compared with the case of the main feature. It is advantageous.
[0036]
As described above, in the case of the first embodiment, the sliding member 24 may be one as shown in FIGS. 1 to 8 or plural as shown in FIGS. 9 to 13 and is not particularly limited. When the plurality of sliding members 24 are connected to each other like the connecting portion 24c of the embodiment shown in FIG. 16 and FIG. The guide rigidity is improved, and the scroll compressor can be made more efficient. Furthermore, if the connecting portion 24c forms a sliding surface with the guide surface 27 as in the embodiment of the figure, the guided area at the both end portions 24a of the sliding member 24 by the guide surface 27 increases. The guide rigidity is improved, and the scroll compressor can be further improved in efficiency.
[0037]
In the embodiment shown in FIGS. 1 to 17, the eccentric portion 26 of the crankshaft 6 has a bearing structure on the female side, and the passive portion 28 on the back surface of the orbiting scroll 30 has a male shape. Accordingly, the orbiting motion of the eccentric portion 26 can be transmitted to the orbiting scroll 30 via the passive portion 28. However, the present invention is not limited to this, and a combination in which males and females are reversed can be used.
[0038]
In addition, the main bearing member 10 as one of the fixed members positioned with the orbiting scroll 30 sandwiched between the fixed scroll 20 and the back surface of the orbiting scroll 30 is brought into close contact with the fixed scroll 20. An annular position holding portion 29 for holding the position is provided. According to this, as shown in FIGS. 1, 4, 5, 11, and 12, the outer peripheral portion of the rear surface of the orbiting scroll 30 is backed up without any other obstacles, and the close contact state with the fixed scroll 20 is improved. Therefore, it becomes easier to prevent overturning than before, and it becomes easy to maintain high efficiency of the scroll compressor. The fixing member is preferably an existing member such as the main bearing member 10 because there is no increase in the number of parts, but another member can be attached and used as necessary.
[0039]
As shown in FIGS. 6 and 13, the orbiting scroll 30 is attached to the main bearing member 10, which is one of the fixing members positioned with the orbiting scroll 30 between the fixed scroll 20 and the fixed scroll 20 via the sliding member 24. If the position holding part 35 is provided to hold it in a close contact position with the fixed scroll 20, both the end parts 24a protruding from the orbiting scroll 30 of the sliding member 24 are used to hold the position as shown in the figure. Since the support force for preventing the rollover is applied to a portion farther from the center of the orbiting scroll 30, that is, the outer diameter position of the orbiting scroll 30, the rollover of the orbiting scroll 30 can be prevented more reliably. The position holding portion 35 in this case is an annular surface formed by a step provided on the peripheral wall of the main bearing member 10, but may be provided in any manner.
[0040]
Further, as shown in FIGS. 7, 8, 14, and 15, the guide surface 27 abuts against both end portions 24a of the sliding member 24, and the abutment surfaces face the outer diameter side, and the fixed scroll 20 side. As the taper surface or the rounded surface gradually approaches, the sliding member 24 receives the frictional resistance P1 toward each end 24a by driving the orbiting scroll 30 and moving in a circular orbit. The guide surface 27 is guided by the tapered surface or the rounded surface and is pressed toward the fixed scroll 20 as indicated by P2 to further increase the degree of adhesion of the orbiting scroll 30 to the fixed scroll 20, so that the scroll compressor can be further improved. Efficiency can be improved.
[0041]
(Embodiment 2)
The second embodiment is shown in FIGS. The rotation prevention mechanism 42 has a maximum circular orbit motion of the orbiting scroll 30 in the first parallel direction 32a, 32a of the outer periphery of the end plate 32 of the orbiting scroll 30 and the first direction X substantially orthogonal to the axial direction of the crankshaft 6. Provided on the main bearing member 10 around the orbiting scroll 30 and the frame-like sliding member 24 in which two parallel sides 24e and 24e are fitted so that they can slide relative to each other with a length exceeding the orbiting diameter R. Thus, the sliding member 24 comes into contact with the projecting side end surfaces 24c of both ends projecting on both sides of the orbiting scroll so as to exceed the orbiting radius R, and both the axial direction of the crankshaft 6 and the first direction are in contact with each other. The sliding member 24 includes a guide surface 27 that guides the sliding member 24 so as to slide within a range equal to or greater than the maximum turning stroke S of the orbiting scroll 30 in a second direction Y that is substantially orthogonal. Since other configurations are not particularly different from those in the first embodiment, the same members are denoted by the same reference numerals, and redundant description is omitted.
[0042]
In this manner, the sliding structure of the sliding member 24 and the orbiting scroll 30 is fitted between the two parallel sides 24e and 24e of the frame-shaped sliding member 24 and the two parallel surfaces 32a and 32a of the outer periphery of the orbiting scroll 30. The embodiment shown in FIG. 1 to FIG. 17 is capable of relative sliding in a range equal to or greater than the maximum turning stroke S of the orbiting scroll 30 in the first direction X substantially perpendicular to the axial direction of the orbiting scroll 30 and the crankshaft 6. Similarly, the sliding member 24 is slidable in the second direction Y substantially perpendicular to the axial direction of the crankshaft 6 and the first direction X between the main bearing member 10 around the orbiting scroll 30. 24 can move with the orbiting scroll 30, and when the circular orbital motion of the eccentric portion is given from the crankshaft 6, the sliding member 24 slides in the first direction X, and the sliding member 24 moves. Second direction with By the synthesis of the sliding of the therewith suction of the refrigerant between the fixed scroll 20 is orbiting driven continuously perform the same orbiting, repeated compression and ejection. In particular, the sliding member 24 has a relative sliding movement with the orbiting scroll 30 due to the fitting between the two parallel sides 24e and 24e and the outer peripheral surfaces 32a and 32a. As a result, the processability, the low cost, and the assemblability are further improved as compared with the case of the main feature.
[0043]
The sliding member 24 is sandwiched between the fixed crawl 20 and the main bearing member 10 so that the sliding member 24 can slide without rattling. However, in this case as well, if the sliding member 24 is designed so as to overlap the end plate 32 of the orbiting scroll 30, a position holding structure such as the embodiment shown in FIGS.
[0044]
【The invention's effect】
According to the present invention, as is apparent from the above description, the orbiting scroll is caused to move circularly with respect to the fixed scroll by the circular orbital motion of the eccentric portion of the crankshaft without rotating via the antirotation mechanism, and the fluid In order to repeatedly perform suction, compression, and discharge, the anti-rotation mechanism is engaged vertically with the orbiting scroll so that the sliding member can slide relative to the orbiting scroll in the first direction, or has a frame shape. Then, it fits with two parallel surfaces of the outer periphery, and both ends of the sliding member are guided in a second direction substantially orthogonal to the first direction by the guide surface of the fixed member provided around the orbiting scroll. Therefore, the workability is good and the required accuracy can be easily secured, and a highly efficient scroll compressor can be obtained. The assembly and cost are excellent.
[Brief description of the drawings]
FIG. 1 is an overall longitudinal sectional view of an example of a scroll compressor according to a first embodiment of the present invention.
2 is an exploded perspective view showing a main structural part of the compressor of FIG. 1; FIG.
3A and 3B are explanatory diagrams showing the operating state of the compressor of FIG. 1, wherein FIG. 3A is a turning state where the orbiting scroll is 0 ° (360 °), FIG. 3B is a turning state of 90 °, and FIG. ) Is a 180 ° turning state, and (d) is a 270 ° turning state.
4 is a cross-sectional view showing a compression mechanism portion of the compressor of FIG. 1. FIG.
FIG. 5 is a cross-sectional view of a compression mechanism portion showing a modification of the embodiment of FIG.
FIG. 6 is a cross-sectional view of a compression mechanism portion showing another modified example of the embodiment of FIG.
7 is a partial cross-sectional view of a compression mechanism portion showing another modified embodiment of the embodiment of FIG.
8 is a partial cross-sectional view of a compression mechanism portion showing another modified example of the embodiment of FIG.
FIG. 9 shows another example of the scroll compressor according to the first embodiment, in which (a) is an exploded perspective view of the main structural part, and (b) is an orbiting scroll and a sliding member. FIG. 3 is a perspective view seen in a different direction.
FIG. 10 is an explanatory diagram showing the operating state of the compressor of FIG. 9, wherein (a) is a turning state where the orbiting scroll is 0 ° (360 °), (b) is a turning state of 90 °, and (c ) Is a 180 ° turning state, and (d) is a 270 ° turning state.
11 is a cross-sectional view showing a compression mechanism portion of the compressor of FIG.
12 is a cross-sectional view of a compression mechanism portion showing a modified embodiment of the embodiment of FIG.
13 is a cross-sectional view of a compression mechanism portion showing another modification of the embodiment of FIG.
14 is a partial cross-sectional view of a compression mechanism portion showing another modified embodiment of the embodiment of FIG.
FIG. 15 is a partial cross-sectional view of a compression mechanism portion showing another modified example of the embodiment of FIG.
FIG. 16 shows another example of the scroll compressor according to the first embodiment, in which (a) is an exploded perspective view of the main structure, and (b) shows the orbiting scroll and the sliding member (a). It is the perspective view seen from a different direction.
FIG. 17 is an explanatory view showing the operating state of the compressor of FIG. 16, in which (a) is a turning state where the orbiting scroll is 0 ° (360 °), (b) is a turning state of 90 °, and (c ) Is a 180 ° turning state, and (d) is a 270 ° turning state.
FIG. 18 is a perspective view of a main structure showing an example of a scroll compressor according to Embodiment 2 of the present invention.
FIG. 19 is an explanatory view showing the operating state of the compressor of FIG. 18, wherein (a) is a turning state where the orbiting scroll is 0 ° (360 °), (b) is a turning state of 90 °, and (c ) Is a 180 ° turning state, and (d) is a 270 ° turning state.
20 is a cross-sectional view showing a compression mechanism portion of the compressor of FIG.
21 is a cross-sectional view of a compression mechanism portion showing a modification of the embodiment of FIG.
FIG. 22 is an exploded perspective view of a main structure portion of a conventional scroll compressor.
FIG. 23 is a cross-sectional view of a rotation prevention mechanism portion of a scroll compressor that employs another conventional rotation prevention method.
FIG. 24 is a cross-sectional view of a rotation prevention mechanism portion of a scroll compressor employing the conventional one rotation prevention method.
25 is a perspective view showing a rollover phenomenon that occurs in the orbiting scroll of the compressor of FIG.
[Explanation of symbols]
2 Compression mechanism
3 Electric motor
6 Crankshaft
20 Fixed scroll
21 feathers
22 End plate
24 Sliding member
24a end
24b End face
24c connecting part
24e 2 sides
25 Through hole
26 Eccentric part
27 Guide plane
28 Passive parts
29, 35 Position holding part
30 Orbiting scroll
31 feathers
32 End plate
34 groove
42 Anti-rotation mechanism
R turning diameter
S Turning stroke

Claims (9)

A fixed scroll that has spiral blades of almost the same shape on one side of the end plate and a rotating scroll are meshed with each other to form a compression chamber between them, and the rotating scroll is prevented from rotating by the circular orbital motion of the eccentric part of the crankshaft. In a scroll compressor that performs circular orbital movement with respect to a fixed scroll without rotating through a mechanism and repeatedly sucks, compresses and discharges fluid,
The anti-spinning mechanism penetrates the end plate of the orbiting scroll in a first direction substantially perpendicular to the axial direction of the crankshaft so as to be able to slide relative to each other with a length exceeding the maximum orbiting diameter of the orbiting scroll's circular orbit. The sliding member and a fixed member around the orbiting scroll are in contact with the projecting side end surfaces of both ends projecting on both sides of the orbiting scroll of the sliding member, and the axial direction of the crankshaft and the first A scroll compressor comprising: a guide surface that guides a sliding member in a second direction substantially orthogonal to both directions so that the sliding member can slide within a range equal to or greater than a maximum turning stroke of the orbiting scroll. . A fixed scroll that has spiral blades of almost the same shape on one side of the end plate and a rotating scroll are meshed with each other to form a compression chamber between them, and the rotating scroll is prevented from rotating by the circular orbital motion of the eccentric part of the crankshaft. In a scroll compressor that performs circular orbital movement with respect to a fixed scroll without rotating through a mechanism and repeatedly sucks, compresses and discharges fluid,
The anti-spinning mechanism has a length exceeding the maximum turning diameter of the circular orbital motion of the orbiting scroll in a first direction substantially perpendicular to the axial direction of the crankshaft through the groove on the back surface of the end plate of the orbiting scroll. A sliding member that is traversed so that it can move, and a fixed member around the orbiting scroll, and is in contact with the projecting side end surfaces of both ends of the orbiting scroll that exceed the orbiting diameter of the sliding member and project on both sides of the orbiting scroll. And a guide surface for guiding the sliding member to slide in a second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction so that the sliding member slides within the range of the maximum turning stroke of the orbiting scroll. A scroll compressor characterized by being configured. The scroll compressor according to any one of claims 1 and 2, wherein one or a plurality of sliding members are provided. The scroll compressor according to claim 3, wherein the plurality of sliding members are connected to each other at the same protruding side at both ends thereof. The scroll compressor according to claim 4, wherein the connecting portion forms a sliding surface with the guide surface. A fixed scroll that has spiral blades of almost the same shape on one side of the end plate and a rotating scroll are meshed with each other to form a compression chamber between them, and the rotating scroll is prevented from rotating by the circular orbital motion of the eccentric part of the crankshaft. In a scroll compressor that performs circular orbital movement with respect to a fixed scroll without rotating through a mechanism and repeatedly sucks, compresses and discharges fluid,
The rotation prevention mechanism has a length exceeding the maximum turning diameter of the circular orbital motion of the orbiting scroll in two parallel surfaces on the outer periphery of the end plate of the orbiting scroll and in a first direction substantially orthogonal to the axial direction of the crankshaft. Frame-shaped sliding members fitted so as to be able to slide relative to each other, and fixed ends around the orbiting scroll, both ends projecting on both sides of the orbiting scroll above the orbiting diameter of the sliding member So that the sliding member slides in the second direction substantially perpendicular to both the axial direction of the crankshaft and the first direction within the range of the maximum turning stroke of the orbiting scroll. A scroll compressor characterized by comprising a guide surface for guiding to the above. A position holding portion is provided on a fixed member positioned with the orbiting scroll sandwiched between the fixed scroll and a position close to the outer diameter of the orbiting scroll so as to hold the orbiting scroll in a close contact position with the fixed scroll. The scroll compressor as described in any one of 1-6. The position holding part which hold | maintains a turning scroll in the contact | adherence position to a fixed scroll via a sliding member was provided in the fixing member located on both sides of a turning scroll between fixed scrolls. The scroll compressor according to item. The guide surfaces are in contact with both ends of the sliding member, and the contact surfaces are tapered surfaces or rounded surfaces that sequentially approach the fixed scroll side toward the outer diameter side. Scroll compressor.

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