JP4649230B2 - Link mechanism and variable capacity compressor - Google Patents

Description

  The present invention relates to a link mechanism capable of relative rotation while transmitting rotational torque, and a variable capacity compressor using the link mechanism.

  The variable capacity compressor is attached to a drive shaft, a rotor that is fixed to the drive shaft and rotates integrally with the drive shaft, and a hinge ball that is slidably attached to the drive shaft, and is tiltable about the hinge ball. The piston stroke can be changed by changing the inclination angle of the swash plate. In order to change the inclination angle of the swash plate while transmitting torque from the rotor to the swash plate, a link mechanism is interposed between the rotor and the swash plate (see, for example, Patent Document 1 and Patent Document 2).

  FIG. 18 shows a conventional link mechanism corresponding to Patent Document 2.

As shown in FIG. 18, the conventional link mechanism includes a pair of opposed rotor arms 145 and 146 that project from the rotor 140 toward the swash plate 141, and one that projects from the swash plate 141 toward the rotor 140. A swash plate arm 147 and a pair of link arms 142A and 142B interposed therebetween are provided. These five arms 145, 142A, 147, 143B, and 146 are stacked in the torque transmission direction, whereby the rotation of the rotor 140 is transmitted to the swash plate. One end of each of the pair of link arms 142A and 142B is rotatably connected to the pair of rotor arms 145 and 146 by the first connecting pin 143, and the other end is connected to the swash plate arm 147 by the second connecting pin. 144 is rotatably connected. As a result, the link arms 142A and 142B rotate with respect to the rotor arms 145 and 146 around the connection pin 143, and the swash plate arm 147 rotates with respect to the link arms 142A and 142B around the connection pin 144. As a result, the inclination angle of the swash plate 141 with respect to the drive shaft (not shown) can be changed.
JP 2003-172417 A JP-A-10-176658

  When the compressor is operated, the contact surface between the rotor arm 145 and the link arm 142A and the contact surface between the link arm 142A and the swash plate arm 147 serve as a torque transmission surface and a rotational sliding surface. That is, the rotor arm 145 and the link arm 142A relatively slide and rotate while receiving a surface pressure due to a large rotational torque. Also, the link arm 142A and the swash plate arm 147 relatively slide and rotate while receiving a surface pressure due to a large rotational torque Ft. Therefore, when the inclination angle of the swash plate 141 is changed, the sliding resistance between the contact surfaces of the rotor arm 145 and the link arm 142A is extremely large, and the contact surface of the link arm 142A and the swash plate arm 147 is large. The sliding resistance between them is extremely large.

  Further, when the compressor is in operation (when the drive shaft rotates), the swash plate 141 receives a compression reaction force Fp from a piston (not shown) connected to the swash plate 141. Since the compression reaction force Fp is shifted forward in the rotational direction from the link mechanism as shown in FIG. 20, a twisting load is applied to the swash plate arm 147 in the Y direction in the drawing, thereby causing the swash plate 141 and the link 142 to have two points ( There is a problem that the sliding resistance is further increased due to biting in such a manner as to “twist” in C, C).

  In order to solve such a problem, in Patent Document 1, washers are interposed between the contact surfaces of the rotor arm and the link arm and between the contact surfaces of the link arm and the swash plate arm. Even so, the problem of “twisting” occurs.

  The present invention has been made based on such a conventional technique, and an object thereof is to provide a link mechanism capable of avoiding an increase in sliding resistance due to twisting and a variable capacity compressor using the link mechanism.

The invention according to claim 1 is a rotating member that is fixed to the drive shaft and rotates integrally, a tilting member that is slidably attached to the drive shaft and is tiltably attached to the drive shaft, A link mechanism that transmits the rotational torque of the rotating member to the tilting member while allowing the tilting member to tilt,
An arm projecting from the rotating member toward the tilting member, an arm projecting from the tilting member toward the rotating member, and an arm of the rotating member and an arm of the tilting member And a link member
A first connecting pin having a slit for inserting the other into one end of the arm of the rotating member or the link member and extending in the rotational torque direction when the other is inserted into the other Are connected to each other rotatably,
The maximum inclination angle generated between the arm of the rotating member and the link member is such that the first connecting pin and the first connecting pin that rotatably support the arm of the rotating member and one end of the link member. It is the maximum inclination angle produced by the clearance with the bearing hole.

The invention according to claim 2 is a rotating member that is fixed to the drive shaft and rotates integrally, a tilting member that is slidably attached to the drive shaft and is tiltably attached to the drive shaft, A link mechanism that transmits the rotational torque of the rotating member to the tilting member while allowing the tilting member to tilt,
An arm projecting from the rotating member toward the tilting member, an arm projecting from the tilting member toward the rotating member, and an arm between the arm of the rotating member and the arm of the tilting member And a link member
A second connection having a slit for inserting the other into one of the arm of the tilting member or the other end of the link member and extending in the rotational torque direction when the other is inserted into the other Are connected to each other by pins,
The maximum inclination angle generated between the arm of the tilting member and the link member is such that the second connection pin and the second connection pin rotatably supporting the arm of the tilting member and the other end of the link member are supported. The maximum inclination angle is caused by the clearance between the pin and the bearing hole.

  The invention according to claim 3 is the link mechanism according to claim 1, wherein the first connecting pin is fixed to a fixing hole provided in one of the arm of the rotating member or the link member. And is supported by the bearing hole provided on the other side.

  The invention according to claim 4 is the link mechanism according to claim 2, wherein the second connecting pin is fixed to a fixing hole provided in one of the arm of the tilting member or the link member. And is supported by the bearing hole provided on the other side.

  A fifth aspect of the present invention is the link mechanism according to any one of the first to fourth aspects, wherein the connecting pin has a constant curvature or gradually a curvature at an axial end portion. It is characterized by having a reduced diameter portion that becomes larger or gradually increases in curvature.

  A sixth aspect of the present invention is the link mechanism according to any one of the first to fourth aspects, wherein the bearing hole has a constant curvature or gradually has a curvature at an end portion in the axial direction. It is characterized by having a diameter-expanded portion that increases or gradually increases in curvature.

  The invention according to claim 7 is the link mechanism according to any one of claims 1 to 6, wherein the slit is provided in the arm of the rotating member, and one end of the link member is inserted into the slit. The slit is provided in the arm of the tilting member, and the other end of the link member is inserted into the slit.

  Invention of Claim 8 is a link mechanism of Claim 7, Comprising: The width dimension of the slit (between a pair of arms) of the said rotation member, The width of the slit (between a pair of arms) of the said tilting member The dimensions are the same.

  The invention according to claim 9 is the link mechanism according to any one of claims 1 to 8, wherein the first connecting pin and the second connecting pin have the same diameter and the same length. It is characterized by.

According to a tenth aspect of the present invention, a drive shaft, a rotating member fixed to the drive shaft and rotating integrally with the drive shaft, a slidably attached to the drive shaft, and a tiltable attachment to the drive shaft. A tilting member, a link mechanism that connects the rotating member and the tilting member to allow tilting of the tilting member, and transmits rotational torque of the rotating member to the tilting member, and rotational motion of the tilting member. A variable capacity compressor having a piston that reciprocates in the cylinder bore,
The link mechanism is
An arm projecting from the rotating member toward the tilting member, an arm projecting from the tilting member toward the rotating member, and an arm of the rotating member and an arm of the tilting member And a link member
A first connecting pin having a slit for inserting the other into one end of the arm of the rotating member or the link member and extending in the rotational torque direction when the other is inserted into the other Are connected to each other rotatably,
The maximum inclination angle generated between the arm of the rotating member and the link member is such that the first connecting pin and the first connecting pin that rotatably support the arm of the rotating member and one end of the link member. It is the maximum inclination angle produced by the clearance with the bearing hole.

According to an eleventh aspect of the present invention, a drive shaft, a rotating member fixed to the drive shaft and rotating integrally, and a slidably attached to the drive shaft and attached to the drive shaft so as to be inclined. A tilting member, a link mechanism that connects the rotating member and the tilting member to allow tilting of the tilting member, and transmits rotational torque of the rotating member to the tilting member, and rotational motion of the tilting member. A variable capacity compressor having a piston that reciprocates in the cylinder bore,
The link mechanism is
An arm projecting from the rotating member toward the tilting member, an arm projecting from the tilting member toward the rotating member, and an arm between the arm of the rotating member and the arm of the tilting member And a link member
A second connection having a slit for inserting the other into one of the arm of the tilting member or the other end of the link member and extending in the rotational torque direction when the other is inserted into the other Are connected to each other by pins,
The maximum inclination angle generated between the arm of the tilting member and the link member is such that the second connection pin and the second connection pin rotatably supporting the arm of the tilting member and the other end of the link member are supported. The maximum inclination angle is caused by the clearance between the pin and the bearing hole.

  A twelfth aspect of the present invention is the variable capacity compressor according to the tenth aspect, wherein the first connecting pin is fixed to a fixing hole provided in one of the arm of the rotating member or the link member. And is supported by the bearing hole provided on the other side.

  The invention according to claim 13 is the variable capacity compressor according to claim 11, wherein the second connecting pin is fixed to a fixing hole provided in one of the arm of the tilting member or the link member. And is supported by the bearing hole provided on the other side.

  A fourteenth aspect of the present invention is the variable capacity compressor according to any one of the tenth to thirteenth aspects of the present invention, wherein the connecting pin has a constant curvature or gradually at the axial end. The present invention is characterized by comprising a reduced-diameter portion in which the curvature increases or the curvature increases stepwise.

  A fifteenth aspect of the present invention is the variable capacity compressor according to any one of the tenth to thirteenth aspects of the present invention, wherein the bearing hole has a constant curvature at the axial end portion or gradually. A diameter-enlarged portion having a curvature that increases or gradually increases in curvature is provided.

  A sixteenth aspect of the present invention is the variable capacity compressor according to any one of the tenth to fifteenth aspects, wherein the slit is provided in an arm of the rotating member, and one end of the link member is provided in the slit. And the slit is provided in the arm of the tilting member, and the other end of the link member is inserted into the slit.

  The invention according to claim 17 is the variable capacity compressor according to claim 16, wherein the width dimension of the slit (between a pair of arms) of the rotating member and the slit (between the pair of arms) of the tilting member. The width dimension is formed to be the same.

  The invention according to claim 18 is the variable capacity compressor according to any one of claims 10 to 17, wherein the first connecting pin and the second connecting pin have the same diameter and the same length. It is characterized by being.

  According to the first and tenth aspects of the present invention, when the link member is tilted to the maximum with respect to the arm of the rotating member, the portion inserted into the slit contacts only one of the opposing surfaces of the slit. Therefore, unlike the conventional case, the portion inserted into the slit does not bite into the opposing surface of the slit so as to “twist” at two points.

  According to invention of Claim 2 and 11, when the link member inclines to the maximum with respect to the arm of a tilting member, the part inserted in the slit contact | abuts only to one of the opposing surfaces of a slit. Therefore, unlike the conventional case, the portion inserted into the slit does not bite into the opposing surface of the slit so as to “twist” at two points.

  According to the third and twelfth aspects of the invention, unlike the structure in which the first connecting pin is pivotally supported by the bearing hole provided in each of the arm of the rotating member and the link member, the design of the link mechanism is facilitated. .

  According to the fourth and thirteenth aspects of the invention, unlike the structure in which the second connecting pin is pivotally supported by the bearing hole provided in each of the arm of the tilting member and the link member, the design of the link mechanism is facilitated. .

  According to the inventions of claims 5 and 14, the same effect as that obtained when the connecting pin is crowned can be obtained. That is, when the connecting pin is tilted within the clearance between the bearing pin and the bearing hole, the reduced diameter portion provided at the axial end of the connecting pin prevents the contact between the connecting pin and the bearing hole locally. .

  According to the sixth and fifteenth aspects of the present invention, the same effect as that obtained when the connecting pin is crowned can be obtained. That is, when the connecting pin is tilted within the clearance range between the bearing hole, the connecting pin and the bearing hole are locally prevented from hitting by the enlarged diameter portion provided at the axial end of the bearing hole. .

  In other words, the structure of the invention of claim 7 and 16 is a pair of arms protruding from the rotating member toward the tilting member and facing each other across the slit, and projecting from the tilting member toward the rotating member and the slit. And a link member inserted between the pair of arms of the rotating member and the pair of arms of the tilting member arranged to face each other. Therefore, in the present invention, five arms that are conventionally stacked in the torque transmission direction are composed of three arms (on the rotating member side, a pair of arms of the rotating member and a link member inserted between them). (The three arms) (on the tilting member side, three arms composed of a pair of arms of the tilting member and a link member inserted therebetween).

  Thereby, even if each member is thickened in the torque transmission direction in order to improve the torque durability of the link mechanism, the entire link mechanism is not enlarged as compared with the conventional structure (for example, Patent Documents 1 and 2). On the other hand, when the size of the link mechanism in the torque transmission direction must be reduced due to layout restrictions in response to a request for downsizing of the device, the conventional structure is maintained with sufficient thickness in the torque transmission direction of each member. Compared to the link mechanism, the size can be greatly reduced.

  According to the inventions of claims 8 and 17, in addition to the effects of claims 6 and 14, since the width dimension of the slit of the rotating member and the width dimension of the slit of the tilting member are formed identically, one end portion is rotated. The link member inserted into the slit of the member and having the other end inserted into the slit of the tilting member can be a simple rectangle. As a result, since the complicated cutting process etc. become unnecessary when manufacturing a link member, the manufacturing cost of a link member is reduced significantly. For example, when the link member is made of aluminum, it can be manufactured by extrusion.

  According to invention of Claim 9 and 18, since the 1st connection pin and the 2nd connection pin are the same diameter and the same length, the 1st connection pin and the 2nd connection pin can be shared. For this reason, the manufacturing cost of a link mechanism is reduced. For example, since the first connecting pin manufacturing mold and the second connecting pin manufacturing mold can be shared, the number of molds is reduced. Further, in the assembly process of the link mechanism, it is not necessary to distinguish the storage positions of the first connection pin and the second connection pin, so that there is an advantage that the burden on the assembly worker is reduced.

  Hereinafter, a variable capacity compressor according to an embodiment of the present invention and a link mechanism used therefor will be described with reference to the drawings.

"Overall structure of variable capacity compressor"
FIG. 1 is an overall cross-sectional view of a variable capacity compressor.

  The compressor 1 of this embodiment is a swash plate type variable capacity compressor as shown in FIG. The variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 arranged at equal intervals in the circumferential direction, and a crank chamber 5 between the cylinder block 2 joined to the front end face of the cylinder block 2. And a rear housing 6 joined to the rear end surface of the cylinder block 2 via a valve plate 9 to form a suction chamber 7 and a discharge chamber 8. The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts B.

  The valve plate 9 includes a suction hole (not shown) that allows the cylinder bore 3 and the suction chamber 7 to communicate with each other, and a discharge hole 12 that allows the cylinder bore 3 and the discharge chamber 8 to communicate with each other.

  A valve mechanism (not shown) for opening and closing the suction hole 11 is provided on the cylinder block 2 side of the valve plate 9, while a valve mechanism (not shown) for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. Is provided. A gasket (not shown) is interposed between the valve plate 9 and the rear housing 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.

  A drive shaft S is supported by bearings 17 and 18 in the support holes 19 and 20 at the centers of the cylinder block 2 and the front housing 4, and the drive shaft S is rotatable in the crank chamber 5.

  In the crank chamber 5, a rotor 21 as a “rotating member” fixed to the drive shaft S, a hinge ball 22 slidably mounted on the drive shaft S, and a tiltable mount on the hinge ball 22 are mounted. And a swash plate 24 as a “tilting member”. The swash plate 24 includes a hub 25 attached to the hinge ball 22 so as to be tiltable and rotatable, and a swash plate body 26 fixed to a boss portion 25a of the hub 25.

  A piston 29 is slidably accommodated in each cylinder bore 3, and the piston 29 is connected to the swash plate 24 via a pair of hemispherical piston shoes 30, 30.

  A link mechanism 40 is interposed between the rotor 21 as the rotating member and the swash plate 24 as the tilting member. The link mechanism 40 allows the rotation of the rotor 21 while allowing the tilt angle of the swash plate 24 to vary. Torque can be transmitted to the swash plate 24. The link mechanism 40 will be described in detail later.

  The inclination angle of the swash plate 24 decreases when the hinge ball 22 moves closer to the cylinder block 2, while the inclination angle of the swash plate 24 decreases when the hinge ball 22 moves away from the cylinder block 2. The angle increases.

  When the drive shaft S rotates, the rotor 21 rotates integrally with the drive shaft S, and the rotation of the rotor 21 is transmitted to the swash plate 24 via the link mechanism 40. The rotation of the swash plate 24 is converted into a reciprocating motion of the piston 29 by the pair of piston shoes 30, 30, and the piston 29 reciprocates in the cylinder bore 3. By the reciprocating motion of the piston 29, the refrigerant in the suction chamber 7 is sucked into the cylinder bore 3 through the suction hole 11 of the valve plate 9 and then compressed in the cylinder block 3, and the compressed refrigerant is discharged into the discharge hole of the valve plate 9. 12 is discharged into the discharge chamber 8.

"Control of variable capacity"
In order to change the discharge capacity of the refrigerant, the piston stroke is changed by changing the inclination angle of the swash plate 24. More specifically, the piston stroke is changed by changing the inclination angle of the swash plate 24 by the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston 29 and the suction chamber pressure Ps on the front surface side of the piston 29. . Therefore, the variable capacity compressor includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8, and this A pressure control mechanism having a control valve 33 that is provided in the middle of the air supply passage and controls opening and closing of the air supply passage is provided. 2 shows the inclined state of the full stroke swash plate 24, FIG. 3 shows the inclined state of the intermediate stroke swash plate 24, and FIG. 4 shows the inclined state of the destroke swash plate 24.

"Linking mechanism"
Next, the link mechanism 40 will be described in detail. FIG. 5 is a perspective view of the link mechanism. 6 is a side view of the link mechanism including a VI-VI cross section in FIG. 2, and FIG. 7 is an enlarged sectional view of the link mechanism 40.

  As shown in FIGS. 5 and 6, the link mechanism 40 includes a pair of arms 41 and 41 that protrude from the rotor 21 toward the swash plate 24 and face each other in the rotational torque transmission direction with the slit 41 s interposed therebetween, and the swash plate 24. A pair of arms 43, 43 projecting from the rotor 21 toward the rotor 21 and facing the rotational torque transmission direction across the slit 43 s, a slit 41 s of the rotor 21 (between the pair of arms 41, 41), and a slit of the swash plate 24 43s (between a pair of arms 43 and 43).

  One end portion 45a of the link member 45 is rotatably connected to the pair of arms 41 and 41 of the rotor 21 by a first connection pin 46 extending in the rotational torque direction, and the other end portion 45b of the link member 45 is The second connecting pin 47 extending in the rotational torque direction is rotatably connected to the pair of arms 43 and 43 of the swash plate 24.

  As shown in FIGS. 6 and 7, a pair of arms 41, 41 of the rotor 21 is provided with a bearing hole 41 a that rotatably supports the first connecting pin 46, and one end 45 a of the link member 45 is provided at one end 45 a. A fixing hole 45c for fixing the first connecting pin 46 by press-fitting is provided. The pair of arms 43, 43 of the swash plate 24 is provided with a bearing hole 43a that rotatably supports the second connecting pin 47, and the other end portion 45b of the link member 45 has a second connecting portion. A fixing hole 45d for fixing the pin 47 by press-fitting is provided. The first connecting pin 46 and the second connecting pin 47 have the same diameter and the same length.

  The width d1 of the slit 41s of the rotor 21 (that is, the width between the inner surfaces 41d and 41d of the pair of arms 41 and 41 of the rotor 21) and the width d2 of the slit 43s of the swash plate 24 (that is, the pair of arms 43 of the swash plate 24). , 43 between the inner side surfaces 43d and 43d) are formed to have the same width. The link member 45 is formed in a rectangular shape, and its outer side surfaces 45e and 45e are formed flush with each other without a step. The width dimension d0 of the link member 45 (that is, the width between the outer side surfaces 45e and 45e of the link member 45) is set narrower than the width d1 of the slit 41s of the rotor 21 and the gap d2 of the slit 43 of the swash plate 24. ing.

  In this embodiment, as shown in FIG. 7, the clearance Δd (= d1-d0) between the slit 41s of the rotor 21 and the link member 45 is set to a predetermined value or more. Accordingly, the maximum inclination angle generated between the rotor arms 41 and 41 and the link member 45 is allowed by the clearance Δd1 (d21−d11) between the first connecting pin 46 and the bearing holes 41a and 41a. The maximum inclination angle. In other words, as shown in FIG. 7, the link member 45 is connected to the arms 41 and 41 of the rotor 21 within a range allowed by the clearance Δd1 (d21−d11) between the first connecting pin 46 and the bearing holes 41a and 41a. Even when tilted to the maximum, the link member 45 does not contact both the opposing surfaces 41d and 41d of the slit 41s, but only contacts one point (point C1 in FIG. 7).

  In this embodiment, the clearance Δd (= d2−d0) between the slit 43s of the swash plate 24 and the link member 45 is set to a predetermined value or more. Thereby, the maximum inclination angle generated between the arm 43 of the swash plate and the link member 45 is allowed by the clearance Δd2 (= d22−d12) between the second connecting pin 47 and the bearing holes 43a and 43a. The maximum inclination angle. In other words, as shown in FIG. 7, the link member 45 with respect to the arms 43 and 43 of the swash plate is within a range allowed by the clearance Δd2 (= d22−d12) between the second connecting pin 47 and the bearing holes 43a and 43a. Is inclined to the maximum, the link member 45 does not come into contact with both of the opposing surfaces 43d and 43d of the slit 43s, but comes into contact with only one point (point C2 in FIG. 7).

"effect"
With the above configuration, this embodiment has the following effects.

  (1) According to the first embodiment, one of the arm 41 of the rotating member 21 or the one end 45a of the link member 45 (in this example, the arm 41 of the rotating member) and the other (in this example, one end 45a of the link member). ), And the other 45a is inserted into the one slit 41s, and these are connected to each other by a first connecting pin 46 extending in the rotational torque direction. . The maximum inclination angle generated between the arm 41 of the rotating member and the link member 45 is the maximum inclination angle generated by the clearance Δd1 (d21-d11) between the first connecting pin 46 and the bearing holes 41a and 41a. It has become. In other words, the link member 45 is inclined to the maximum with respect to the arm 41 of the rotating member within the allowable range of the clearance Δd1 (d21-d11) between the first connecting pin 46 and the bearing holes 41a, 41a. In addition, the portion inserted into the slit 41s (in this example, one end portion 45a of the link member 45) does not simultaneously contact both surfaces 41d and 41d of the opposing surface of the slit 41s, but contacts only one surface 41d. That is, unlike the conventional structures (for example, Patent Documents 1 and 2), they do not bite into each other so as to be “twisted” at two points.

  (2) According to the first embodiment, one of the arm 43 of the tilting member 25 or the other end 45b of the link member 45 (in this example, the arm 43 of the tilting member) and the other (in this example, the other end of the link member). A slit 43s for inserting the portion 45b), and the other 45 is inserted into the one 43, and these are connected to each other by a second connecting pin 47 extending in the rotational torque direction. . The maximum inclination angle generated between the arm 43 of the tilting member and the link member 45 is the maximum inclination generated by the clearance Δd2 (= d22−d12) between the second connecting pin 47 and the bearing holes 43a and 43a. It is a horn. In other words, the link member 45 is inclined to the maximum with respect to the arm 43 of the tilting member within the allowable range of the clearance Δd2 (= d22−d12) between the second connecting pin 47 and the bearing holes 43a and 43a. However, the portion inserted into the slit 43s (the other end 45b of the link member 45) does not simultaneously contact both surfaces of the facing surfaces 43d and 43d of the slit 43s, and one surface of the facing surfaces 43d and 43d of the slit 43s. Abuts only on. That is, unlike conventional structures (for example, Patent Documents 1 and 2), they do not bite into each other so that they are “twisted” at two points.

  (3) According to the first embodiment, the first connecting pin 46 is fixed to the fixing hole 45c provided in one of the arm 41 of the rotating member or the link member 45 (in this example, the link member 45). And is supported by bearing holes 41a and 41a provided on the other side (in this example, the arm 41 of the rotating member). For this reason, for example, unlike the structure in which the bearing holes are provided in each of the arm and the link member of the rotating member and the first connecting pin is pivotally supported in these bearing holes, one of them is the fixed hole 45c, so the design of the link mechanism is easy. It becomes.

  (4) According to the first embodiment, the second connecting pin 47 is fixed to the fixing hole 45d provided in one of the arm 43 of the tilting member or the link member 45 (in this example, the link member 45). And is supported by bearing holes 43a and 43a provided on the other side (in this example, the arm 43 of the tilting member). Therefore, for example, unlike the structure in which bearing holes are provided in each of the arm and link member of the tilting member and the second connecting pin is pivotally supported in these bearing holes, one of them is the fixed hole 45d, so that the design of the link mechanism is easy. It becomes.

  (5) According to the first embodiment, the slit 41s is provided in the arm 41 of the rotating member, the one end 45a of the link member 45 is inserted into the slit 41s, and the slit 43s is provided in the arm 43 of the tilting member. The other end 45b of the link member 45 is inserted into the slit 43s. In other words, a pair of arms 43 and 43 projecting from the rotating member 21 toward the tilting member 25 and facing each other across the slit 41s, and projecting from the tilting member 25 toward the rotating member 21 and sandwiching the slit 43s. And a link member 45 inserted between the pair of arms 41 and 41 of the rotating member and the pair of arms 43 and 43 of the tilt member.

  Therefore, in the conventional structure (for example, Patent Documents 1 and 2), five arms are stacked in the torque transmission direction. In this embodiment, three arms (on the rotating member side, a pair of arms 41 and 41 of the rotating member and Three arms 41, 45, 41 composed of a link member 45 inserted between them (on the tilt member side, a pair of arms 43, 43 of the tilt member and a link member 45 inserted between them) 3 arms 43, 45, 43).

  Thereby, even if each member (41, 43, 45) is thickened in the torque transmission direction in order to improve the torque durability of the link mechanism 40, the link mechanism 40 as a whole does not become larger than the conventional structure. On the other hand, when the size of the link mechanism 40 in the torque transmission direction must be reduced due to layout restrictions, etc., the conventional structure with sufficient thickness in the torque transmission direction of each member (41, 43, 45) is secured. Compared to the above, the link mechanism 40 can be greatly reduced in size.

  (6) According to the first embodiment, the width dimension d1 of the slit 41s of the arms 41 and 41 of the rotating member and the width dimension d2 of the slit 43s of the arms 43 and 43 of the tilt member are formed to be the same. Therefore, the width dimension d1 of the slit 41s of the arm 41, 41 of the rotating member and the width dimension d2 of the slit 43s of the arm 43, 43 of the tilt member are formed to be the same. Therefore, the link member 45 can be a simple rectangle. As a result, the manufacturing cost of the link member 45 is greatly reduced because complicated cutting or the like is not required when the link member 45 is manufactured. For example, when the link member 45 is made of aluminum, it can be manufactured by extrusion molding or the like.

  (7) According to the first embodiment, the first connecting pin 46 and the second connecting pin 47 have the same diameter and the same length. Therefore, the first connecting pin 46 and the second connecting pin 47 can be shared, and the manufacturing cost of the link mechanism 40 can be reduced. For example, since the manufacturing mold for the first connecting pin 46 and the manufacturing mold for the second connecting pin 47 can be shared, the number of molds is reduced. Further, in the assembly process of the link mechanism 40, it is not necessary to distinguish the placement positions of the first connection pin 46 and the second connection pin 47 on the workbench, so that there is an advantage that the burden on the assembly worker is reduced.

  Hereinafter, modifications of the first embodiment and other embodiments will be described. In addition, the same code | symbol is attached | subjected about the same or similar structure as the above-mentioned 1st Embodiment, and description is abbreviate | omitted about a structure and its effect.

First modification of the first embodiment
8 to 10 show a first modification of the link mechanism of the first embodiment.

  In the first modified example, the axially ends of the connecting pins 46 and 47 are provided with a reduced diameter portion 60 that has a constant curvature, gradually increases in curvature, or gradually increases in curvature. . That is, the connecting pins 46 and 47 are crowned. In addition, the code | symbol 61 in FIG. 10 is a linear part of the front end side from the reduced diameter part 60 which curves. According to this modification, when the link member 45 is inclined within the allowable range of the clearance between the connection pins 46 and 47 and the bearing holes 41a and 41a, the connection pins 46 and 47 are 47 and the bearing holes 41a, 41a are increased in contact area, and the two are prevented from intermingling. The radius of curvature is set based on the material of the connecting pin and the arm and the surface pressure generated between the connecting pin and the bearing hole. However, the radius of curvature is preferably larger than the axial length of the connecting pins 46 and 47.

Second Modification of First Embodiment FIGS. 11 and 12 show a second modification of the link mechanism of the first embodiment.

  In the second modification, the diameter-expanded portion 70 has a constant curvature, gradually increases the curvature, or gradually increases in curvature at the axial ends of the bearing holes 41a, 41a and 43a, 43a. It has. Therefore, the same effect as that obtained when the connecting pins 46 and 47 are crowned can be obtained. According to the second modified example, when the connection pins 46 and 47 are inclined within the clearance range between the bearing holes 41a and 43a, the connection pins 46 and 47 and the bearings are formed at the edge portion. The contact area with the holes 41a and 43a is increased, and the two are prevented from intermingling.

Second Embodiment Next, a second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment, the holes 41a and 41a provided in the arms 41 and 41 of the rotating member are fixing holes for press-fitting and fixing the first connecting pin 46, and the hole 45c provided in the link member 45 is the first. The bearing hole for pivotally supporting the connecting pin 46 is opposite to the first embodiment. Further, the holes 43a and 43a provided in the arms 43 and 43 of the tilting member are fixing holes for press-fitting and fixing the second connecting pin 47, and the hole 45c provided in the link member 45 serves as a shaft for the second connecting pin 47. This is the opposite of the first embodiment in that it is a bearing hole to be supported. Other structures are the same as those in the first embodiment. Therefore, according to the second embodiment, the same function and effect as the first embodiment can be obtained.

Modification of Second Embodiment FIGS. 14 and 15 show a modification of the second embodiment.

  In this modified example, a diameter-expanded portion 80 having a constant curvature, gradually increasing curvature, or gradually increasing curvature at the axial ends of the bearing holes 45c and 45d provided in the link member 45. It has. Therefore, the same effect as that obtained when the connecting pins 46 and 47 are crowned can be obtained. That is, according to this modification, when the connecting pins 46 and 47 are tilted within the clearance range between the bearing holes 45c and 45d, the connection pins 46 and 47 and the bearing holes 45c and 45d are formed at the edge portion. The contact area is increased and the two are prevented from intermingling.

  In the embodiment described above, the width dimension d1 of the slit 41S (between the pair of arms 41 and 41) of the rotor 21 and the width dimension d2 of the slit 43S (between the pair of arms 43 and 43) of the swash plate 24 are formed identically. In the present invention, for example, as shown in FIGS. 16 and 17, the width dimension d1 of the slit 41S (between a pair of arms) of the rotor 21 is set. Different from the width dimension d2 of the slit 43S (between a pair of arms) of the swash plate, the link members 45B and 45C may be formed in a convex shape.

  In the above-described embodiment, the rectangular link member 45 is inserted into the slit 41s (between the pair of arms 41 and 41) of the rotor 21 and the slit 43s (between the pair of arms 43 and 43) of the swash plate. However, in the present invention, for example, as shown in FIG. 18, from a single arm 41 and a swash plate 24 projecting from the rotor 21 in slits 45s, 45s of a link member 45D formed in a substantially H shape. A structure in which one projecting arm 43 is inserted may be used. Further, for example, as shown in FIG. 19, one arm 43 projecting from the swash plate 24 is inserted into the slit 45 s of the other end 45 b of the link member 45 E formed in a substantially Y shape, and the rotor 21 The structure may be such that one end portion 45a of the link member 45 is inserted into the slit 41s (between the pair of arms 41, 41).

  Note that the present invention is not limited to the embodiment described above.

  In the present invention, when the link is tilted to the maximum extent within the range allowed by the clearance between the bearing hole and the connecting pin, the portion inserted into the slit contacts only one of the opposing surfaces of the slit. If it is a structure, the 1st connection pin may be pivotally supported by each of the arm and link member of a rotation member, and the 2nd connection pin is pivotally supported by each of the arm and link member of a rotation member. May be.

  The bearing hole may be a bottomed hole.

  In the above-described embodiment, the connection pin is fixed to the fixing hole by press fitting. However, in the present invention, the connection pin may be fixed to the fixing hole by screwing or other means.

  In the present invention, the first connecting pin may be integrally formed with either the arm or the link member of the rotating member, and the second connecting pin may be either the arm of the tilting member or the link member. It may be integrally molded.

  In the above-described embodiment, the swash plate 24 is configured by combining the swash plate body 26 and the hub 25 which are separate members. However, in the present invention, for example, the swash plate 24 formed in advance may be used.

  In the above-described embodiment, the swash plate 24 is attached to the drive shaft 10 via the sleeve 22. However, in the present invention, for example, the swash plate 24 is directly attached to the drive shaft 10 without a sleeve. May be.

  In the above-described embodiment, a swash type swash plate is used, but a wobble type swash plate may be used in the present invention.

  In addition, the present invention can be implemented in various other modes as long as they belong to the technical scope of the present invention.

FIG. 1 is a sectional view of a variable capacity compressor having a link mechanism according to a first embodiment of the present invention. FIG. 2 is a diagram for explaining a full stroke state of a swash plate of the variable capacity compressor. FIG. 3 is a diagram illustrating an intermediate stroke state of the variable capacity compressor. FIG. 4 is a diagram for explaining a destroke state of the variable capacity compressor. FIG. 5 is a perspective view showing a connection structure between a rotor and a swash plate of the variable capacity compressor. 6 is a side view including a VI-VI cross section in FIG. 2 showing a connection structure between a rotor and a swash plate of the variable capacity compressor. FIG. 7 is an enlarged sectional view of the link mechanism. FIG. 8 is a cross-sectional view showing a first modification of the link mechanism of the first embodiment. 9 is a side view of a connecting pin with a crowning of the link mechanism shown in FIG. FIG. 10 is an enlarged view of a portion X in FIG. FIG. 11 is a cross-sectional view showing a second modification of the link mechanism of the first embodiment. 12 is an enlarged cross-sectional view of a rotor or swash plate arm of the link mechanism of FIG. FIG. 13 is a cross-sectional view showing the link mechanism of the second embodiment. FIG. 14 is a cross-sectional view showing a modification of the link mechanism of the second embodiment. 15 is a cross-sectional view of a link member of the link mechanism shown in FIG. FIG. 16 is a view showing a modification of the link mechanism of the first embodiment and the second embodiment. FIG. 17 is a view showing a modification of the link mechanism of the first embodiment and the second embodiment. FIG. 18 is a view showing a modification of the link mechanism of the first embodiment and the second embodiment. FIG. 19 is a view showing a modification of the link mechanism of the first embodiment and the second embodiment. FIG. 20 is a diagram showing an example of a conventional link mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Variable capacity compressor 21 ... Rotor (rotating member)
22 ... Hinge ball 24 ... Swash plate (tilting member)
DESCRIPTION OF SYMBOLS 29 ... Piston 40 ... Link mechanism 41, 41 ... A pair of arms 43, 43 ... A pair of arms 45 ... Link 45a ... One end part 45b ... Other end part 46 ... 1st connection pin 47 ... 2nd connection pin S ... Drive Shaft d0: Link member width d1: Slit width (interval between a pair of arms)
d2: slit width (interval between a pair of arms)

Claims (18)

A rotating member (21) fixed to the drive shaft (S) and rotated integrally with the drive shaft (S), and a tilt attached to the drive shaft (S) so as to be slidable and attached to the drive shaft (S) in a tiltable manner. A link mechanism (40, 40B, 40C) for transmitting the rotational torque of the rotating member (21) to the tilting member (24) while connecting the member (24) and allowing the tilting member (24) to tilt. 40D, 40E),
An arm (41) protruding from the rotating member (21) toward the tilting member (24), and an arm (43) protruding from the tilting member (24) toward the rotating member (21) And a link member (45) interposed between the arm (41) of the rotating member and the arm (43) of the tilting member,
One of the arms of the rotating member or one end (41 or 45a) of the link member has a slit (41s or 45s) for inserting the other (45a or 41), and the other is inserted into the other And these are rotatably connected to each other by a first connecting pin (46) extending in the direction of rotational torque,
The maximum inclination angle generated between the arm (41) of the rotating member and the link member (45) is the first connecting pin that rotatably supports the arm of the rotating member and one end of the link member. (46) and a link mechanism (40, 40B, 40C, 40D, 40E) having a maximum inclination angle caused by a clearance between the bearing hole (41a and / or 45c) of the first connecting pin. A rotating member (21) fixed to the drive shaft (S) and rotated integrally with the drive shaft (S), and a tilt attached to the drive shaft (S) so as to be slidable and attached to the drive shaft (S) in a tiltable manner. A link mechanism (40, 40B, 40C) for transmitting the rotational torque of the rotating member (21) to the tilting member (24) while connecting the member (24) and allowing the tilting member (24) to tilt. 40D, 40E),
An arm (41) protruding from the rotating member (21) toward the tilting member (24), and an arm (43) protruding from the tilting member (24) toward the rotating member (21) And a link member (45) interposed between the arm (41) of the rotating member and the arm (43) of the tilting member,
One end (43 or 45b) of the arm of the tilting member or the link member has a slit (41s or 45s) for inserting the other (45b or 43), and the other is inserted into the other In the state, these are rotatably connected to each other by the second connecting pin (47) extending in the rotational torque direction,
The maximum inclination angle generated between the arm (43) of the tilting member and the link member (45) is the second connection that rotatably supports the arm of the tilting member and the other end of the link member. Link mechanism (40, 40B, 40C, 40D, 40E) characterized by a maximum inclination angle caused by a clearance between the pin (47) and the bearing hole (43a and / or 45d) of the second connecting pin . The link mechanism (40, 40B, 40C, 40D, 40E) according to claim 1,
The first connecting pin (46) is fixed to a fixing hole provided in one of the arm (41) of the rotating member or the link member (45) and is pivoted to the bearing hole provided in the other. A link mechanism (40, 40B, 40C, 40D, 40E) characterized by being supported. The link mechanism (40, 40B, 40C, 40D, 40E) according to claim 2,
The second connecting pin (47) is fixed to a fixing hole provided in one of the arm (43) of the tilting member or the link member (45) and is pivoted to the bearing hole provided in the other. A link mechanism (40, 40B, 40C, 40D, 40E) characterized by being supported. The link mechanism (40, 40B, 40C, 40D, 40E) according to any one of claims 1 to 4,
The connecting pin (46, 47) is provided with a reduced diameter portion (60) having a constant curvature or a gradually increasing curvature or a gradually increasing curvature at an axial end portion. Link mechanism (40, 40B, 40C, 40D, 40E). The link mechanism (40, 40B, 40C, 40D, 40E) according to any one of claims 1 to 4,
The bearing hole (41a or 45c, 43a or 45d) has a constant diameter or a diameter-expanded portion (70 or 80) whose curvature gradually increases or gradually increases at the axial end. A link mechanism (40, 40B, 40C, 40D, 40E) characterized by comprising: The link mechanism (40) according to any one of claims 1 to 6,
The arm (41) of the rotating member is provided with the slit (41s), and one end (45a) of the link member (45) is inserted into the slit (41s) and the arm (43) of the tilting member is inserted. The link mechanism (40), wherein the slit (43s) is provided, and the other end (45b) of the link member (45) is inserted into the slit (43s). Link mechanism (40) according to claim 7,
The link mechanism (40), wherein the width dimension of the slit (41s) of the rotating member and the width dimension of the slit (43s) of the tilt member are formed to be the same. The link mechanism (40) according to any one of claims 1 to 8,
The link mechanism (40), wherein the first connecting pin (46) and the second connecting pin (47) have the same diameter and the same length. A drive shaft (S), a rotating member (21) fixed to the drive shaft (S) and rotating integrally therewith, and slidably attached to the drive shaft (S) and with respect to the drive shaft (S) The tilting member (24) attached in a tiltable manner, the rotating member (21) and the tilting member (24) are connected to allow the tilting member (24) to tilt while allowing the rotating member (21) to be tilted. Link mechanism (40, 40B, 40C, 40D, 40E) that transmits the rotational torque of the tilting member (24), and a piston that reciprocates in the cylinder bore (3) as the tilting member (24) rotates. (29), a variable capacity compressor (1) comprising:
The link mechanism (40, 40B, 40C, 40D, 40E)
An arm (41) protruding from the rotating member (21) toward the tilting member (24), and an arm (43) protruding from the tilting member (24) toward the rotating member (21) And a link member (45) interposed between the arm (41) of the rotating member (21) and the arm (43) of the tilting member (24),
One of the arms of the rotating member or one end (41 or 45a) of the link member has a slit (41s or 45s) for inserting the other (45a or 41), and the other is inserted into the other And these are rotatably connected to each other by a first connecting pin (46) extending in the direction of rotational torque,
The maximum inclination angle generated between the arm (41) of the rotating member and the link member (45) is the first connecting pin that rotatably supports the arm of the rotating member and one end of the link member. The variable capacity compressor (1), characterized by a maximum inclination angle generated by a clearance between (46) and the bearing hole (41a and / or 45c) of the first connecting pin. A drive shaft (S), a rotating member (21) fixed to the drive shaft (S) and rotating integrally therewith, and slidably attached to the drive shaft (S) and with respect to the drive shaft (S) The tilting member (24) attached in a tiltable manner, the rotating member (21) and the tilting member (24) are connected to allow the tilting member (24) to tilt while allowing the rotating member (21) to be tilted. Link mechanism (40, 40B, 40C, 40D, 40E) that transmits the rotational torque of the tilting member (24), and a piston that reciprocates in the cylinder bore (3) as the tilting member (24) rotates. (29), a variable capacity compressor (1) comprising:
The link mechanism (40, 40B, 40C, 40D, 40E)
An arm (41) protruding from the rotating member (21) toward the tilting member (24), and an arm (43) protruding from the tilting member (24) toward the rotating member (21) And a link member (45) interposed between the arm (41) of the rotating member (21) and the arm (43) of the tilting member (24),
One end (43 or 45b) of the arm of the tilting member or the link member has a slit (41s or 45s) for inserting the other (45b or 43), and the other is inserted into the other In the state, these are rotatably connected to each other by the second connecting pin (47) extending in the rotational torque direction,
The maximum inclination angle generated between the arm (43) of the tilting member and the link member (45) is the second connection that rotatably supports the arm of the tilting member and the other end of the link member. A variable capacity compressor (1) characterized by a maximum inclination angle caused by a clearance between a pin (47) and a bearing hole (43a and / or 45d) of the second connecting pin. A variable capacity compressor (1) according to claim 10,
The first connecting pin (46) is fixed to a fixing hole provided in one of the arm (41) of the rotating member or the link member (45) and is pivoted to the bearing hole provided in the other. A variable capacity compressor characterized by being supported. A variable capacity compressor (1) according to claim 11,
The second connecting pin (47) is fixed to a fixing hole provided in one of the arm (43) of the tilting member or the link member (45) and is pivoted to the bearing hole provided in the other. A variable capacity compressor (1) characterized by being supported. The variable capacity compressor (1) according to any one of claims 10 to 13,
The connecting pin (46, 47) is provided with a reduced diameter portion (60) having a constant curvature or a gradually increasing curvature or a gradually increasing curvature at an axial end portion. A variable capacity compressor (1). The variable capacity compressor (1) according to any one of claims 10 to 13,
The bearing hole (41a or 45c, 43a or 45d) has a constant diameter or a diameter-expanded portion (70 or 80) whose curvature gradually increases or gradually increases at the axial end. A variable capacity compressor (1) comprising: The variable capacity compressor (1) according to any one of claims 10 to 15,
The arm (41) of the rotating member is provided with the slit (41s), and one end (45a) of the link member (45) is inserted into the slit (41s) and the arm (43) of the tilting member is inserted. The variable capacity compressor (1), wherein the slit (43s) is provided, and the other end (45b) of the link member (45) is inserted into the slit (43s). A variable capacity compressor (1) according to claim 16, comprising:
The variable capacity compressor (1), wherein the width dimension of the slit (41s) of the rotating member and the width dimension of the slit (43s) of the tilt member are formed to be the same. A variable capacity compressor (1) according to any one of claims 10 to 17,
The variable capacity compressor (1), wherein the first connecting pin (46) and the second connecting pin (47) have the same diameter and the same length.

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