JP2010150944A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor including a swing link mechanism setting a swing operation range with a high degree of accuracy as much as possible and improving durability. <P>SOLUTION: This scroll compressor 30 includes: a fixed scroll 40; a movable scroll 42 forming a compression chamber 44 by being turned while being engaged with the fixed scroll 40; and the swing link mechanism 73 turning the movable scroll 42 so as to vary a turning radius by swinging a bush 72 around a drive pin 66 decentered with respect to a rotating shaft 60. The swing link mechanism 73 has: a recessed section 77 formed on the side of the rotating shaft 60; a projection 75 formed on the side of the bush 72; and a shock-absorbing section 79 storing an elastic member 87 interposed in a section with the projection 75 fitted into the recessed section 77 and absorbing shock when the projection 75 abuts on the recessed section 77. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a scroll compressor including a swing link mechanism that makes a turning radius of a movable scroll variable.

  Generally, a scroll compressor is configured to include a fixed scroll having a spiral fixed wrap and a rotary scroll having a spiral swing wrap meshing with the fixed wrap inside a housing. Then, by rotating and driving the rotary drive shaft with a drive source such as a motor or an engine, and turning the orbiting scroll via a drive pin provided eccentrically from the axis of the rotation drive shaft, the fixed scroll and the orbiting scroll A compression chamber is formed in between, and the fluid is compressed by moving the compression chamber gradually from the outer peripheral portion to the central portion.

  By the way, in this kind of scroll type compressor, the structure provided with the turning radius variable mechanism which makes the turning radius of a turning scroll variable may be used. If the turning radius variable mechanism is provided, it is possible to obtain effects such as prevention of breakage of the fixed wrap and the turning wrap at a high load due to liquid compression and the like, and improvement in contact between the fixed wrap and the turning wrap.

  In such a turning radius variable mechanism, a method called a swing link mechanism is such that a turning scroll is turned through an eccentric bush pivotally supported by the drive pin, and a protrusion and a protrusion are provided between the eccentric bush and the rotary drive shaft. A recess into which is inserted is interposed. As a result, the turning radius of the eccentric bush, that is, the orbiting scroll is made variable, and when the amount of change of the turning radius exceeds the predetermined range, the protrusion and the recess are brought into contact and regulated. That is, in the swing link mechanism, the turning radius of the orbiting scroll is configured to be variable within a predetermined range so that the orbiting scroll is not compressed due to excessive swing motion or the like, or the fixed lap and the orbiting lap are excessively or insufficiently contacted. Etc. can be avoided.

  As a scroll type compressor provided with a swing link mechanism, Patent Document 1 discloses a configuration in which a soft material is attached to either a protrusion or a recess that regulates the range of swing motion. This is to prevent abnormal noise and vibration due to collision between the protrusion and the recess caused by unintended swing motion that occurs when the compressor is started or stopped.

Japanese Utility Model Publication No. 59-107081

  By the way, in the case of the configuration described in Patent Document 1, the soft material attached to one of the protrusions or the recesses contacts the other, in other words, the limit of the swing range by the soft material formed of synthetic resin or the like. Is set. For this reason, deformation such as crushing of the soft material, variation in dimensions, and the like may occur, and it is difficult to accurately set and manage the swing range. Furthermore, since the portion that finally receives the impact of the orbiting scroll is the soft material, the soft material is likely to be deteriorated or damaged due to long-term use, and the durability may be inferior.

  The present invention has been made in consideration of the above-described conventional problems, and provides a scroll compressor having a swing link mechanism that can set the range of swing operation with high accuracy and can improve durability. The purpose is to provide.

  A scroll compressor according to the present invention includes a fixed scroll, a movable scroll that is rotated while meshing with the fixed scroll, and forms a compression chamber together with the fixed scroll, and an eccentric bush centered on a drive pin that is eccentric from the rotary drive shaft. A scroll type compressor having a swing link mechanism for swinging the movable scroll by a swing radius by swinging the swing, wherein the swing link mechanism is formed on an opposing surface of the rotary drive shaft and the eccentric bush. A protrusion formed on one side, a recess formed on the other of the opposing surfaces, the protrusion being inserted and contacting the protrusion to restrict the swing motion, and the protrusion and the recess being fitted An impact member is provided at the mating portion and accommodates an elastic member that cushions an impact when the projection and the recess come into contact with each other. And the elastic member is compressed between the protrusion and the recess in accordance with a swing motion of the eccentric bush, and the protrusion is formed when the elastic member reaches a predetermined compression rate. The swing movement limit position is defined by the contact of the concave portion with the concave portion.

  According to such a configuration, by providing the shock buffering portion in the swing link mechanism for turning the movable scroll so that the turning radius is variable, the elastic member accommodated in the shock buffering portion elastically receives the swing motion of the eccentric bush. Eventually, when the elastic member has a predetermined compression rate, the protrusion and the recess come into contact with each other to define the swing range. That is, since the limit position of the final swing motion is defined by the contact between the protrusion and the recess, the swing range can be set with high accuracy. Furthermore, since it is not necessary to receive the impact of the abutment only with an elastic member, the elastic member can be used in an arbitrary compression rate range as appropriate, and its damage and deterioration are effectively prevented and durability is improved. Can be improved.

  Further, the impact buffering portion has an annular space formed in the fitting portion and the elastic member having an annular shape that can be accommodated in the annular space, and an outer peripheral surface that abuts on the concave portion of the protrusion. The radius is referred to as r, the radius of the inner peripheral surface in contact with the outer peripheral surface of the concave portion is referred to as R, the width dimension in the radial direction of the annular space is referred to as A, and R> r, A> R− It may be set so as to satisfy the relational expression of r. That is, for example, by setting the protrusion swing range “Rr” to be smaller than the width dimension A of the annular space containing an elastic member made of a rubber material, for example, swinging from the eccentric bush to the protrusion by liquid compression or the like. Even when a sudden force is generated in the direction, first, in a state where the protrusion is in the “R-r” which is the swing range, the protrusion swings smoothly while the shock is buffered by the elastic force of the elastic member. Then, the elastic member is compressed to a predetermined compression rate, so that the protrusion and the recess come into contact with each other, and the swing motion is restricted. Therefore, the sudden force can be received only with the elastic material to the end, and the elastic member can be effectively avoided from being damaged.

  Furthermore, when the outer diameter of the annular space is referred to as Do, by setting so as to satisfy the relational expression of Do> 2 · R, for example, under a condition where a larger elastic force is required for the elastic member. However, it is possible to increase the volume of the elastic member made of, for example, a rubber-based elastic body, without enlarging the entire recess, by forming only an annular space for accommodating the elastic member. In addition, since the volume of the elastic member can be increased by expanding the annular space to the concave side instead of reducing the diameter of the protrusion, the diameter of the protrusion that receives the swinging motion of the eccentric bush is made sufficiently large. It is possible to secure and improve the strength.

  Furthermore, when the inner diameter of the annular space is referred to as Di, by setting so as to satisfy the relation of Di> 2.multidot.r, for example, even when a larger elastic force is required for the elastic member. Without increasing the entire protrusion, only the diameter Di of the base can be formed large, the volume of the elastic member can be increased, and the strength of the protrusion can be ensured. In addition, since it is not necessary to increase the diameter of the entire protrusion, the minimum size of the concave portion on the other side is sufficient, and it is not necessary to drill a hole excessively, and the strength of the member formed with the concave portion is increased. Can be secured, and the number of processing steps can be reduced.

  In addition, a narrowed portion is provided in a part of the annular space by forming a reinforcing portion having an enlarged diameter at the base end portion of the protrusion, and extending the reinforcing portion to a surface facing the annular space. If it comprises, the intensity | strength of a processus | protrusion can be improved, and the protrusion of the elastic member outside the annular space can be effectively prevented by the narrow portion.

  Further, when a chamfer is provided at a corner formed between the annular space and the contact surface of the protrusion and the recess, for example, the protrusion is swung to the swing limit from the origin position direction. When returning to the step, it is possible to effectively avoid the elastic member from being caught between the protrusion and the recess.

  According to the present invention, by providing the shock buffering portion in the swing link mechanism for turning the movable scroll so that the turning radius is variable, the elastic member accommodated in the shock buffering portion can elastically receive the swing motion of the eccentric bush. Eventually, when the elastic member has a predetermined compression rate, the protrusion and the recess come into contact with each other to define the limit position of the swing motion. That is, since the final swing limit is defined by the contact between the protrusion and the recess, the swing range can be set with high accuracy. Furthermore, since it is not necessary to receive the impact of the abutment only with an elastic member, the elastic member can be used in an arbitrary compression rate range as appropriate, and its damage and deterioration are effectively prevented and durability is improved. Can be improved.

  Hereinafter, preferred embodiments of a scroll compressor according to the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 is a cross-sectional view along the axial direction of a scroll compressor 30 according to an embodiment of the present invention, and FIG. 2 is a partial cross-sectional exploded perspective view of the scroll compressor 30 shown in FIG. The scroll compressor 30 according to the present embodiment constitutes an air conditioning unit such as a vehicle or a building, and sucks and compresses a predetermined gas (refrigerant gas) under the driving action of a driving source such as an engine or a motor (not shown). And a compressor for discharging.

  As shown in FIGS. 1 and 2, the scroll compressor 30 includes a front housing 32 formed in a cup shape and a rear housing 34 formed in a crown shape. In the upper part of the front housing 32, for example, a suction port 32a for introducing a gas made of a refrigerant gas or the like into the inside thereof is formed. On the other hand, at the upper part of the rear housing 34, a discharge port 34a for discharging the compressed gas, which is compressed by the scroll compressor 30, to the refrigerant circulation system, for example, is formed. The front housing 32 is provided with a plurality of attachment seats 32b for attaching the scroll compressor 30 to, for example, an engine or an external device.

  Inside the front housing 32, a fixed scroll 40 and a movable scroll (orbiting scroll) 42 that rotates with respect to the fixed scroll 40 are disposed.

  The fixed scroll 40 is erected in a spiral shape from a fixed side substrate portion 40b including an outer peripheral edge portion 40a sandwiched between the front housing 32 and the rear housing 34, and from the fixed side substrate portion 40b to the movable scroll 42 side. And a fixed spiral wall (fixed wrap) 40c. The movable scroll 42 is provided with a movable-side substrate portion 42a, a movable-side spiral wall (movable wrap) 42b that is erected in a spiral shape from the movable-side substrate portion 42a toward the fixed scroll 40, and meshes with the fixed-side spiral wall 40c. Have

  A compression chamber (gas compression chamber) 44 is formed by the fixed-side substrate portion 40 b and the fixed-side spiral wall 40 c of the fixed scroll 40 and the movable-side substrate portion 42 a and the movable-side spiral wall 42 b of the movable scroll 42. In order to seal the compression chamber 44, a seal member 46 is attached to each end of the fixed-side spiral wall 40c and the movable-side spiral wall 42b so as to be in sliding contact with the movable-side substrate portion 42a and the fixed-side substrate portion 40b, respectively. It is worn. The seal member 46 is made of, for example, PPS (polyphenylene sulfide), carbon fiber, and a solid lubricant.

  A rear housing 34 is mounted on the back surface 40d of the fixed scroll 40 via a gasket 48 formed in an annular shape and in a thin plate shape, whereby a gas discharge chamber 50 communicating with the discharge port 34a is formed. A compressed gas outlet hole 40 e that communicates from the compression chamber 44 to the gas discharge chamber 50 is formed at a substantially central portion of the fixed-side substrate portion 40 b of the fixed scroll 40.

  The rear housing 34, the fixed scroll 40, and the gasket 48 are fastened to the front housing 32 by a plurality of (for example, four) bolts 52. At that time, an O-ring 56 that seals the gas suction chamber 54 formed by the fixed scroll 40 and the front housing 32 is attached to the annular groove 40f formed in the fixed-side substrate portion 40b of the fixed scroll 40. .

  The back surface 40d of the fixed scroll 40 closes the compressed gas lead-out hole 40e, and when the compressed gas compressed in the compression chamber 44 reaches a predetermined high pressure, the gas is bent and opened. A discharge valve 58 for leading compressed gas to the discharge chamber 50 is provided. The opening degree of the discharge valve 58 is regulated by a retainer portion 48 a formed in the gasket 48. The retainer portion 48a is received by a receiving portion 34b formed of an inclined surface formed inside the rear housing 34.

  A shaft portion 60a at one end of a rotary shaft 60 that is a rotational drive shaft (crankshaft) is inserted into the opening 32c at the reduced diameter end portion of the front housing 32. The shaft portion 60a is rotatably supported by the opening 32c via the first bearing 61. On the other hand, the other end of the rotating shaft 60 is provided with a support 62 that expands in diameter. The support body 62 is rotatably supported when the support surface 62 a on the outer peripheral side surface is fitted into the second bearing 64. The second bearing 64 is supported by a shoulder portion 32 d formed on the front housing 32.

  As shown in FIG. 3, a drive pin 66 is fixed to the support body 62 around an axis Q1 that is eccentric to the axis Q0 (axis Q0 of the rotary shaft 60). A sealing member 68 for sealing the gas suction chamber 54 is fitted into the shaft portion 60a of the rotary shaft 60. The sealing member 68 is supported by the opening shoulder 32e of the front housing 32, and is configured by, for example, covering a ring-shaped core made of a metal material with a rubber-based material or a resin-based material.

  The movable side substrate portion 42a of the movable scroll 42 is formed with a circular concave portion 42d opened on the front surface 42c side. A bush (eccentric bush) 72 is rotatably inserted into the circular recess 42 d via a swivel bearing 70. The bush 72 is pivoted so as to be swingable by the rotary shaft 60 by inserting the drive pin 66 into a hole 72a formed eccentrically with the shaft center thereof, and thereby the movable scroll 42 is pivoted with a variable turning radius. Let

  Such a bush 72 can swing while the amount of change in the turning radius is restricted within a predetermined range by a swing link mechanism 73 described later. That is, the movable scroll 42 can be turned within the predetermined range by the bush 72. It is configured.

  An annular groove 66a is formed at the tip of the drive pin 66, and a C-shaped retaining ring 74 is fitted into the annular groove 66a. Accordingly, the bush 72 is configured to be rotatable about the drive pin 66 in a state in which the drive pin 66 is prevented from coming off in the axial direction by the C-shaped retaining ring 74. A balance weight 76 is mounted near the base of the drive pin 66 via a bush 72.

  Thrust for supporting the movable scroll 42 slidably (turnable) by the sliding contact surface 80a between the movable side substrate portion 42a of the movable scroll 42 and the annular support portion 32f formed inside the front housing 32. One direction orthogonal to the axial direction of the rotating shaft 60, and an Oldham ring (orbiting ring) 82 that is a rotation restraining member that constrains the rotation of the movable scroll 42 while the plate 80 restrains the rotation of the movable scroll 42. And an Oldham base 84 which is a rotation restraining member that receives the axial thrust force applied to the movable scroll 42 via the thrust plate 80. Arranged.

  A pair of first engaging recesses 90 and 90 that allow the movable scroll 42 to reciprocate only in one radial direction are formed on the front surface 42c side of the movable side substrate portion 42a of the movable scroll 42. A pair of first engaging convex portions 92 and 92 formed in one radial direction of the Oldham ring 82 are slidably engaged with the first engaging concave portions 90. Further, in order to allow the movable scroll 42 to reciprocate only in the direction orthogonal to the first engagement recess 90, the Oldham ring 82 has a radial direction orthogonal to the first engagement protrusion 92. A pair of protruding second engaging convex portions 94, 94 are formed (see FIG. 2). The second engaging convex portions 94 are slidably engaged with a pair of second engaging concave portions 96 and 96 formed in one radial direction of the Oldham base 84.

  The Oldham base 84 is formed with a notch 84a extending along the radial direction of the Oldham base 84 and avoiding interference with the Oldham ring 82 while allowing the Oldham ring 82 to reciprocate. (See FIG. 2). On the other hand, on the back side of the first engagement convex portion 92 of the Oldham ring 82, that is, on the notch 84a side of the Oldham base 84, the Oldham ring 82 bulges in the radial direction and the first engagement convex portion in the circumferential direction. A bulging portion 92 a that slightly bulges from both side surfaces of 92 is formed. The bulging portion 92 a is disposed to face the notch 84 a of the Oldham base 84.

  Further, the Oldham base 84 has the shim 86 interposed therebetween and a plurality of (for example, two) bolts 88 attached to a fastening through hole 84c formed in the notch 84a. It is fixed to 32f. With this configuration, the Oldham base 84 can be fixed to the support portion 32 f of the front housing 32 while avoiding the bolt 88 from interfering with the thrust plate 80. The shim 86 is interposed to adjust the axial gap between the fixed scroll 40 and the movable scroll 42 to a predetermined value, and should not be interposed when the gap is adjusted appropriately. Also good.

  A pulley 102 is attached to the outer peripheral portion of the opening 32 c of the front housing 32 via a third bearing 100. That is, the rotational force is transmitted to the pulley 102 from a rotational drive source such as an engine (not shown), and the electromagnetic clutch 104 is turned ON / OFF, whereby the rotational force is transmitted to and disconnected from the rotational shaft 60 that is the rotational drive shaft. Is done.

  The balance weight 76 includes an outer peripheral portion 76 a formed in a substantially semicircular plate shape, and a fitting insertion portion 76 b that is a portion to be attached to the bush 72. The balance weight 76 is formed by the inner peripheral surface 84f of the Oldham base 84 and the inner wall surface 32i of the support portion 32f in the front housing 32, and is disposed so as to rotate in a region where interference with the Oldham ring 82 is avoided. ing. As a result, the balance weight 76 also turns along with the turning of the movable scroll 42, that is, a centrifugal force that balances the centrifugal force generated by the turning of the movable scroll 42 is generated by the balance weight 76, and the movable scroll 42 moves excessively toward the fixed scroll 40. It is possible to effectively avoid the occurrence of excessive frictional force and the like, and to stabilize the turning of the movable scroll 42. As a method for attaching the balance weight 76 to the bush 72, in addition to the press-fitting by the fitting portion 76b as described above, for example, riveting or the like may be used, and further, the balance weight 76 may be formed integrally with the bush 72.

  FIG. 3 is an enlarged cross-sectional view of the swing link mechanism 73 and its peripheral portion shown in FIG. 4A is an explanatory diagram schematically showing the swing link mechanism 73 shown in FIG. 3 in an enlarged manner, and FIG. 4B shows a state in which the bush 72 is swung to the maximum from the state shown in FIG. 4A. It is explanatory drawing. FIG. 5 is a partially omitted cross-sectional view taken along line VV in FIG. 4A.

  The swing link mechanism 73 has a protrusion (swing range restriction protrusion) 75 protruding from a surface 72 b of the bush 72 facing the support body 62, and the bush 72 of the support body 62 fixed to one end of the rotary shaft 60. A cylindrical recess (fitting recess) 77 formed on the surface 62b, into which the protrusion 75 is inserted with a predetermined fitting intersection (gap), and the bush 72 swings to form the protrusion 75 and the recess 77. And an impact buffering portion 79 for buffering an impact at the time of contact.

  The protrusion 75 includes a columnar base portion (small diameter portion) 81 provided on the base end side, and a disk-shaped contact portion (large diameter portion) 83 provided on the distal end side with a larger diameter than the base portion 81. This is a stepped shaft member. The impact buffering portion 79 includes an annular space 85 formed between the inner peripheral surface 77 a of the concave portion 77 and the outer peripheral surface 81 a of the base portion 81 at the fitting portion between the projection 75 and the concave portion 77, and the annular space 85. And an annular elastic member 87 mounted thereon. As the elastic member 87, for example, a ring-shaped rubber-based elastic body, a ring-shaped leaf spring member, or the like can be used. In short, the impact of the protrusion 75 due to the swing motion of the bush 72 is reduced to a predetermined compression rate. Any member that can be received by force may be used.

  As shown in FIG. 3, in the case of this embodiment, the projection 75 and the recess 77 have the same axis Q2 when the bush 72 is not swinging. Of course, the axis of the projection 75 and the recess 77 is the same. The centers may be eccentric from each other, and the axis Q2 may be coaxial with the axis Q0 of the rotary shaft 60.

  As can be understood from FIGS. 4A, 4B, and 5, in such a swing link mechanism 73, the inner diameter of the recess 77 is set to be sufficiently larger than the outer diameter of the protrusion 75 (the outer diameter of the contact portion 83). In other words, the protrusion 75 and the recess 77 are fitted by a gap fit having a predetermined intersection, and the protrusion 75 passes through the recess 77 under the elastic action of the elastic member 87 interposed in the annular space 85. It is movable. Therefore, in the bush 72, the elastic member 87 is compressed to the maximum, in other words, the elastic member 87 is compressed to a predetermined compression rate (compression amount), and the outer peripheral surface (contact surface) 83a of the contact portion 83 is recessed. It is possible to perform a swing motion within a range until it abuts on the inner peripheral surface (abutment surface) 77a of 77 (see FIGS. 4B and 5).

Therefore, as shown in FIG. 4A, in the swing link mechanism 73, the radius of the outer peripheral surface 83a of the contact portion 83 that contacts the recess 77 in the protrusion 75 is referred to as r, and the inner periphery that contacts the outer peripheral surface 83a in the recess 77. When the radius of the surface 77a is referred to as R and the width dimension in the radial direction of the annular space 85 is referred to as A, assuming that "R>r", the radius r, the radius R, and the width dimension A are expressed by the following formula (1 ) To satisfy the relationship.
A> Rr (1)

  That is, the relational expression (1) indicates that the swing range “R−” is a range in which the protrusion 75 (bush 72) can move in the compression direction of the elastic member 87 rather than the width A of the annular space 85 that houses the elastic member 87. r ”is set to be small.

  Next, the operation of the scroll compressor 30 according to the present embodiment basically configured as described above will be described.

  Under the action of the electromagnetic clutch 104, when a rotational force is transmitted from the engine or the like (not shown) to the rotary shaft 60 that is a rotational drive shaft, the support body 62 rotates through the second bearing 64 and is fixed to the support body 62. The driven drive pin 66 turns in a state of being eccentric with respect to the axis of the rotary shaft 60. As a result, the bush 72 turns, under the sliding action of the Oldham ring 82 slidably supported by the Oldham base 84, and under the rotation restraining action of the Oldham ring 82, and the sliding contact surface 80a of the thrust plate 80. Under the sliding support action, the movable scroll 42 turns with respect to the fixed scroll 40 while being restricted from rotating. At this time, the balance weight 76 is turning by generating a centrifugal force that balances the centrifugal force generated by the turning of the movable scroll 42.

  As a result, the compression chamber 44 formed between the fixed scroll 40 and the movable scroll 42 gradually advances from the outer peripheral portion to the central portion, and is introduced into the gas suction chamber 54 under the sealing action of the seal member 46. The gas is compressed. The compressed gas thus compressed is led out from the compressed gas outlet hole 40e to the gas discharge chamber 50, and is discharged to a refrigerant circulation system (not shown) through the discharge port 34a.

  During such a compression operation (including when starting and stopping), for example, when liquid compression occurs in the compression chamber 44, the swing direction from the movable scroll 42 to the bush 72 (see arrows in FIGS. 4B and 5). A sudden and excessive force is generated in the projection 75, and a similar force is also generated in the protrusion 75 that receives this force.

  Therefore, in the scroll compressor 30 according to the present embodiment, based on the relational expression (1), in the swing link mechanism 73, the swing range “of the protrusion 75 is larger than the width dimension A of the annular space 85 that houses the elastic member 87. “R−r” is set small. Thereby, in the swing link mechanism 73, even when a sudden force as described above is generated, first, when the protrusion 75 is in the swing range “Rr”, the protrusion 75 (bush 72). Is smoothly swung while the shock is buffered by the elastic force of the elastic member 87. Next, when the elastic member 87 is compressed to a predetermined compression rate (compression amount), the outer peripheral surface 83a of the contact portion 83 of the projection 75 and the inner peripheral surface 77a of the concave portion 77 are in contact with each other. Be regulated.

  That is, in the swing link mechanism 73, the swing movement of the bush 72 can be elastically received by the compression of the elastic member 87 constituting the impact buffering portion 79, and finally the protrusion 75 and the recess 77 abut. Defines the limit position of the swing motion. Therefore, the swing range of the bush 72 can be accurately set by appropriately setting the swing range “R−r”. In the above relational expression (1), how small the swing range “R−r” is set with respect to the width dimension A of the annular space 85 depends on the dimensions and characteristics of the rubber material forming the elastic member 87. It may be set as appropriate in consideration.

  In addition, since the final swing limit is defined by the contact between the protrusion 75 and the recess 77, it is not necessary to receive the above-mentioned impact only with the elastic member 87, and the damage and deterioration of the elastic member 87 can be effectively performed. Can be prevented. In other words, the swing link mechanism 73 is configured such that the protrusion 75 and the recess 77 are brought into contact with each other when the elastic member 87 reaches a predetermined compression rate. In consideration of the elastic force and the like, it can be used as appropriate in an arbitrary compression rate range (elastic region), and as a result, the durability of the elastic member 87 can be improved.

  Further, in the swing link mechanism 73, an impact buffering portion 79 composed of the annular space 85 and the elastic member 87 is provided using a fitting portion between the protrusion 75 and the recess 77. For this reason, for example, it is not necessary to separately provide the impact buffering portion 79 on the outer surface of the bush 72, etc., space saving can be achieved, and the scroll compressor 30 can be reduced in size.

  In the scroll compressor 30 according to this embodiment, the swing link mechanism 73 can be configured as, for example, a swing link mechanism 73a shown in FIG. FIG. 6 is an explanatory diagram of the swing link mechanism 73a and its peripheral part according to a first modification of the swing link mechanism 73. FIG. In FIG. 6, the same reference numerals as those shown in FIGS. 1 to 5 indicate the same or similar configurations, and therefore the detailed description thereof is omitted as they exhibit the same or similar functions and effects. The same shall apply.

  As shown in FIG. 6, the swing link mechanism 73 a is a protrusion having a contact portion (large diameter portion) 110 having substantially the same shape as the contact portion 83 on the base end side of the base portion 81 instead of the protrusion 75. The swing range restricting projection) 112 is provided.

  Therefore, in the swing link mechanism 73 a, the outer peripheral surfaces 83 a and 110 a that are the contact surfaces of the pair of contact portions 83 and 110 simultaneously contact the inner peripheral surface 77 a that is the contact surface of the recess 77. For this reason, even when a sudden force in the swing direction is generated in the bush 72 due to the above-described liquid compression or the like, the force is applied by the two contact portions 83 and 110 on the proximal end side and the distal end side of the protrusion 112. Since it can be received, the swing range can be regulated more reliably and stably. In addition, since the load due to the contact with the recess 77 is more evenly applied in the axial direction, the protrusion 112 can more effectively avoid damage and deformation of the protrusion 112.

  In the scroll compressor 30 according to the present embodiment, the swing link mechanism 73 can also be configured as a swing link mechanism 73b shown in FIG. 7A. FIG. 7A is an explanatory diagram of a swing link mechanism 73b according to a second modification of the swing link mechanism 73 and its peripheral portion, and FIG. 7B is a state in which the bush 72 is swung to the maximum from the state shown in FIG. 7A. It is explanatory drawing which shows.

  As shown in FIG. 7A, in the swing link mechanism 73b, a protrusion (swing range regulating protrusion) 114, a recess (fitting recess) 116, and an impact buffer 118 are used instead of the protrusion 75, the recess 77, and the impact buffer 79. It consists of the structure which provided.

  The protrusion 114 is not a stepped shape like the protrusion 75 but a substantially cylindrical shaft member. Of the outer peripheral surface of the projection 114, the outer peripheral surface 114 a on the proximal end side forms the annular space 122 of the shock absorbing portion 118, while the distal end side functions as an abutment surface 114 b that abuts on the recess 116. The recess 116 includes a large diameter portion (elastic member placement portion) 119 positioned on the outer peripheral surface 114a side of the protrusion 114, and a small diameter portion (on the contact surface 114b side of the protrusion 114) that is smaller in diameter than the large diameter portion 119. It is a stepped shape constituted by 120). The shock absorbing portion 118 is formed between the outer peripheral surface 114a and the inner peripheral surface 119a of the large diameter portion 119 at the fitting portion between the outer peripheral surface 114a side of the protrusion 114 and the large diameter portion 119 of the concave portion 116. An annular space 122 and an elastic member 87 interposed in the annular space 122 are configured.

  In such a swing link mechanism 73b, as can be understood from FIGS. 7A and 7B, the contact surface 114b on the distal end side of the protrusion 114 and the inner peripheral surface 120a of the small diameter portion 120 of the recess 116 are in contact with each other, The swing limit of the bush 72 is defined.

Therefore, as shown in FIG. 7A, in the swing link mechanism 73b, the radius of the contact surface 114b (outer peripheral surface 114a) that contacts the recess 116 in the protrusion 114 is substantially the same as in the case of the swing link mechanism 73 shown in FIG. 4A. The radius of the inner peripheral surface (contact surface) 120a of the small-diameter portion 120 that contacts the contact surface 114b in the recess 116 is referred to as R (diameter is 2 · R). When the width dimension is referred to as A and the outer diameter of the annular space 122 is referred to as Do, the radius R and the outer diameter Do are represented by the following equation together with the relationship “A> R−r” shown in the relational expression (1). It is set so as to satisfy the relationship (2).
Do> 2 · R (2)

  That is, the relational expression (2) indicates that the outer diameter Do of the annular space 122 that accommodates the elastic member 87 is larger than the inner diameter “2 · R” of the small diameter portion 120 of the concave portion 116 that constitutes the contact surface with the protrusion 114. It stipulates that it should be set large. In other words, the above relational expression (2) configures the large-diameter portion 119 constituting the annular space 122 in which the elastic member 87 is disposed in the recess 116 to be larger in diameter than the small-diameter portion 120 in contact with the protrusion 114. It stipulates.

  Therefore, for example, the bush 72 is expected to receive a more rapid force in the swing direction due to the use conditions of the scroll compressor 30, and a larger elastic force is required for the elastic member 87. However, it is possible to increase the volume of the elastic member 87 made of a rubber-based elastic body, for example, by forming only the annular space 122 for accommodating the elastic member 87 without enlarging the entire recess 116 including the contact surface. It becomes. Further, since the volume of the elastic member 87 can be increased by expanding the annular space 122 toward the concave portion 116 instead of reducing the diameter of the protrusion 114, the diameter of the protrusion 114 that receives the swing motion of the bush 72 is increased. A sufficient size can be secured, and the strength can be secured and improved.

  In the scroll compressor 30 according to the present embodiment, the swing link mechanism 73 can also be configured as a swing link mechanism 73c shown in FIG. FIG. 8 is an explanatory diagram of the swing link mechanism 73c and its peripheral part according to a third modification of the swing link mechanism 73. FIG.

  As shown in FIG. 8, the swing link mechanism 73 c has a projection (swing range regulating projection) 124, a recess (fitting recess) 126, and an impact buffering portion 128 instead of the projection 75, the recess 77 and the impact buffering portion 79. It consists of the structure which provided.

  The protrusion 124 is provided on the base end side, and a base portion (large diameter portion) 132 constituting the annular space 130 of the shock absorbing portion 128 and a contact portion (small diameter portion) 134 provided on the distal end side and having a smaller diameter than the base portion 132. Is a stepped shaft member. The concave portion 126 has a large-diameter portion (elastic member placement portion) 136 corresponding to the base portion 132 of the protrusion 124 and a small-diameter portion (contact portion) corresponding to the contact portion 134 of the protrusion 124 having a smaller diameter than the large-diameter portion 136. 138 and a stepped shape. The shock absorbing portion 128 is formed between the outer peripheral surface 132a of the base portion 132 and the inner peripheral surface 136a of the large diameter portion 136 at the fitting portion between the base portion 132 of the protrusion 124 and the large diameter portion 136 of the recess portion 126. An annular space 130 and an elastic member 87 interposed in the annular space 130.

  In such a swing link mechanism 73 c, as can be understood from FIG. 8, the outer peripheral surface (contact surface) 134 a of the contact portion 134 in the protrusion 124 and the inner peripheral surface (contact surface) of the small diameter portion 138 in the recess 126. 138a abut each other, and the swing limit of the bush 72 is defined.

Therefore, as shown in FIG. 8, in the swing link mechanism 73c, the radius of the outer peripheral surface 134a that abuts the recess 126 in the protrusion 124 is set to r (diameter is 2 · diameter), as in the case of the swing link mechanism 73b shown in FIG. 7A. r), the radius of the inner peripheral surface 138a of the small diameter portion 138 that contacts the outer peripheral surface 134a in the concave portion 126 is referred to as R (diameter is 2 · R), and the width dimension in the radial direction of the annular space 130 is A. In addition, when the outer diameter of the annular space 130 is referred to as Do and the outer diameter of the base portion 132 constituting the annular space 130 of the protrusion 124 is referred to as Di, “A> R−r” shown in the relational expression (1) above. And the relationship “Do> 2 · R” shown in the relational expression (2), the radius r and the outer diameter Di are set to satisfy the relation of the following expression (3).
Di> 2 · r (3)

  That is, the relational expression (3) indicates that the inner diameter Di of the annular space 130 that accommodates the elastic member 87 is larger than the outer diameter “2 · r” of the contact portion 134 of the protrusion 124 that constitutes the contact surface with the recess 126. Is set to be large. In other words, the above relational expression (3) is such that the base portion 132 constituting the annular space 130 in which the elastic member 87 is disposed in the protrusion 124 is larger in diameter than the contact portion 134 that contacts the recess 126. Is stipulated.

  Therefore, for example, the bush 72 is expected to receive a more rapid force in the swing direction due to the use conditions of the scroll compressor 30, and a larger elastic force is required for the elastic member 87. However, it is possible to increase only the diameter Di of the base (base 132) without increasing the entire protrusion 124 including the contact surface, and to increase the volume of the elastic member 87 made of, for example, a rubber-based elastic body. It becomes possible. In addition, by forming the base portion 132 on the base end side of the protrusion 124, the strength of the protrusion 124 to which a large force is applied in the swing direction by contact with the elastic member 87 and the concave portion 126 can be ensured. At the same time, since it is not necessary to increase the diameter of the entire protrusion 124, the minimum size of the concave portion 126 on the other side is sufficient, and it is not necessary to drill an excessively large hole. The strength of the body 62 can be ensured, and the number of processing steps can be reduced.

  By the way, in such a swing link mechanism 73, 73a-73c, for example, as shown in FIGS. 9A and 9B, if an R shape or a chamfered portion is formed at the base of the protrusion, the corner of the recess, or the like, its durability Etc. can be further improved. FIG. 9A is an explanatory view of a swing link mechanism 73d according to a modification of the swing link mechanism 73b shown in FIG. 7A and its peripheral part. FIG. 9B shows that the bush 72 is swung to the maximum from the state shown in FIG. 9A. It is explanatory drawing which shows a state.

  As shown in FIG. 9A, the swing link mechanism 73d is provided with a protrusion 140, a recess 142, and an impact buffering portion 144 instead of the projection 114, the recess 116, and the impact buffering portion 118 that constitute the swing link mechanism 73b shown in FIG. 7A. Consisting of

  The protrusion 140 has substantially the same shape as the protrusion 114 (see FIG. 7A), but a reinforcing portion 146 having an R shape or a taper shape and having an enlarged diameter is formed at the base (base end portion). The concave portion 142 has substantially the same shape as the concave portion 116 (see FIG. 7A), and has a large diameter portion (elastic member placement portion) 148 positioned on the proximal end side of the protrusion 140 and a small diameter portion positioned on the distal end side of the protrusion 140. (Contact portion) 150 is a stepped shape. A tapered chamfered portion 154 is formed at the corner (edge) of the small diameter portion 150 facing the annular space 152. The shock absorbing portion 144 is formed between the outer peripheral surface 140a of the protrusion 140 and the inner peripheral surface 148a of the large diameter portion 148 at the fitting portion between the base end side of the protrusion 140 and the large diameter portion 148 of the concave portion 142. An annular space 152 and an elastic member 87 interposed in the annular space 152 are configured.

  As can be understood from FIGS. 9A and 9B, the reinforcing portion 146 formed at the base of the protrusion 140 is formed to extend to the inner peripheral surface 148 a that is a surface facing the annular space 152. As a result, the annular space 152 includes a portion having a width dimension A between the outer peripheral surface 140a of the protrusion 140 and the inner peripheral surface 148a of the large-diameter portion 148, and part of the reinforcing portion 146 and the inner peripheral surface 148a. And a narrow portion (narrow portion) 156 having a width B smaller than the width A.

  Therefore, as shown in FIG. 9B, in the state where the bush 72 is swung to the swing limit and the projection 140 and the small diameter portion 150 are in contact with each other, the annular space 152 is compressed by the portion of the width dimension A containing the elastic member 87. Thus, the width dimension A1 is obtained. Then, the elastic member 87 is usually crushed so as to extend in a direction along the outer peripheral surface 140a and the inner peripheral surface 148a (see FIG. 9B). However, depending on the state of the swing motion, the elastic member 87 may be between the bush 72 and the support body 62. May move so as to protrude into the gap G1.

  Therefore, in the swing link mechanism 73d, since the narrow portion 156 is provided by the reinforcing portion 146, when the bush 72 is swung to the limit as shown in FIG. 9B, the narrow portion 156 is further narrowed. The width B1 is obtained, and the protrusion of the elastic member 87 into the gap G1 is effectively prevented.

  Moreover, since the base of the protrusion 140 is reinforced by expanding the diameter by the reinforcing portion 146, the strength of the protrusion 140 can be improved. Furthermore, since it can reinforce without enlarging the diameter of the whole protrusion 140, the necessary size of the concave portion 142 on the other side is sufficient, and there is no need to drill a hole excessively. For this reason, the strength of the support body 62 in which the concave portion 142 is formed can be sufficiently secured, and the number of processing steps can be reduced.

  On the other hand, since the chamfered portion 154 is provided in the concave portion 142, for example, when the bush 72 as shown in FIG. 9B is swung to the swing limit, the state is returned to the non-swinging state as shown in FIG. 9A. 9B, it is possible to effectively avoid the elastic member 87 from being caught in the gap G2 formed between the protrusion 140 and the recess 142 shown in FIG. 9B.

  It goes without saying that such a reinforcing part and chamfered part can be applied to the swing link mechanism according to each embodiment shown in FIGS. 4A, 6, 7 </ b> A and 8. For example, in the case of the swing link mechanisms 73 and 73a shown in FIGS. 4A and 6, if the chamfered portion is formed at the corner (edge) facing the annular space 85 of the contact portions 83 and 110, the elastic member as described above. 87 has an effect of preventing biting, and if a reinforcing portion is provided at the base of the protrusions 75 and 112, the effects of improving the strength and preventing the elastic member from protruding can be obtained. In the swing link mechanism 73c shown in FIG. 8, for example, when a reinforcing portion or a chamfered portion is provided at the corner portion of the base portion 132 of the protrusion 124 or a chamfered portion is provided at the corner portion of the small diameter portion 138 of the concave portion 126, Effects such as improvement in strength, prevention of protruding elastic members, prevention of biting, and the like can be obtained.

  In the swing link mechanism 73 or the like as the turning radius variable mechanism in the above embodiment, the protrusion is provided on the bush 72 side and the recess is provided on the support body 62 side of the rotary shaft 60, but the recess is provided on the bush side. It is good also as a structure which provided the convex part in the support body side. For example, in the case of the swing link mechanism 73 shown in FIG. 4A, as shown in FIG. 10, a recess 77 is provided on the bush 72 side, and a projection 75 protruding from the support body 62 is fitted into the recess 77. The swing link mechanism 73e can be configured, and the same applies to the other swing link mechanisms 73a to 73d.

  The present invention is not limited to the above-described embodiment, and it is needless to say that various configurations can be adopted without departing from the gist of the present invention.

  For example, the elastic member that constitutes the impact buffering portion that cushions the impact caused by the contact between the protrusion and the recess may be other than the ring shape, that is, a plurality of rod-like elastic members are arranged along the annular space. What is necessary is just a shape and a material which can buffer (absorb) the impact appropriately until the projection and the recess come into contact.

It is sectional drawing which follows the axial direction of the scroll compressor which concerns on one Embodiment of this invention. It is a partial cross-section exploded perspective view of the scroll compressor shown in FIG. It is sectional drawing to which the swing link mechanism shown in FIG. 1 and its peripheral part were expanded. 4A is an explanatory diagram schematically showing the swing link mechanism shown in FIG. 3 in an enlarged manner, and FIG. 4B is an explanatory diagram showing a state in which the bush is swung to the maximum from the state shown in FIG. 4A. . 4B is a partially omitted cross-sectional view taken along line VV in FIG. 4A. FIG. It is explanatory drawing of the swing link mechanism which concerns on the 1st modification of the swing link mechanism shown to FIG. 4A, and its peripheral part. FIG. 7A is an explanatory diagram of a swing link mechanism according to a second modification of the swing link mechanism shown in FIG. 4A and its peripheral part. FIG. 7B shows that the bush is swung to the maximum from the state shown in FIG. 7A. It is explanatory drawing which shows a state. It is explanatory drawing of the swing link mechanism which concerns on the 3rd modification of the swing link mechanism shown to FIG. 4A, and its peripheral part. FIG. 9A is an explanatory diagram of a swing link mechanism and its peripheral part according to a modification of the swing link mechanism shown in FIG. 7A, and FIG. 9B shows a state where the bush is swung to the maximum from the state shown in FIG. 9A. It is explanatory drawing. It is sectional drawing to which the swing link mechanism which concerns on the 4th modification of the swing link mechanism shown in FIG. 3, and its peripheral part were expanded.

Explanation of symbols

DESCRIPTION OF SYMBOLS 30 ... Scroll type compressor 40 ... Fixed scroll 40c ... Fixed side spiral wall 42 ... Movable scroll 42b ... Movable side spiral wall 44 ... Compression chamber 60 ... Rotating shaft 62 ... Support body 62b, 72b ... Opposite surface 66 ... Drive pin 72 ... bush
73, 73a to 73e ... Swing link mechanisms 75, 112, 114, 124, 140 ... Protrusions 77, 116, 126, 142 ... Recesses 79, 118, 128, 144 ... Shock absorbing parts 85, 122, 130, 152 ... Annular space 87 ... Elastic member 146 ... Reinforcement part 154 ... Chamfering part 156 ... Narrow part

Claims (6)

With fixed scrolling,
A movable scroll that is turned while meshing with the fixed scroll and forms a compression chamber together with the fixed scroll;
A swing link mechanism for swinging the movable scroll with a swing radius variable by swinging the eccentric bush about a drive pin eccentric from the rotational drive shaft;
A scroll type compressor comprising:
The swing link mechanism includes a protrusion formed on one of opposing surfaces of the rotational drive shaft and the eccentric bush,
A recess that is formed on the other of the opposing surfaces and that restricts the swing motion by being in contact with the protrusion and inserting the protrusion;
An impact buffering portion that is provided in a fitting portion between the projection and the recess and accommodates an elastic member that cushions an impact when the projection and the recess contact each other;
Have
The elastic member is compressed between the protrusion and the concave portion in accordance with the swing motion of the eccentric bush, and the protrusion and the concave portion abut when the elastic member reaches a predetermined compression rate. Thus, the limit position of the swing motion is defined. The scroll compressor according to claim 1, wherein
The impact buffer portion includes an annular space formed in the fitting portion, and the elastic member having an annular shape that can be accommodated in the annular space,
The radius of the outer peripheral surface that contacts the concave portion of the protrusion is referred to as r, the radius of the inner peripheral surface that contacts the outer peripheral surface of the concave portion is referred to as R, and the width dimension in the radial direction of the annular space is referred to as A. , R> r,
A> Rr
A scroll compressor characterized by satisfying the relational expression The scroll compressor according to claim 2,
When the outer diameter of the annular space is referred to as Do,
Do> 2 ・ R
A scroll compressor characterized by satisfying the relational expression The scroll compressor according to claim 2 or 3,
When the inner diameter of the annular space is called Di,
Di> 2 · r
A scroll compressor characterized by satisfying the relational expression In the scroll compressor according to any one of claims 2 to 4,
Forming a reinforced portion with an enlarged diameter at the base end of the protrusion;
A scroll compressor characterized in that a narrow portion is provided in a part of the annular space by extending the reinforcing portion to a surface facing the annular space. In the scroll type compressor according to any one of claims 2 to 5,
A scroll compressor, wherein a chamfered portion is provided at a corner portion formed between the annular space and the contact surfaces of the protrusion and the recess.

Images