JP2019124161A - Compressor - Google Patents

Abstract

To provide a compressor with a torque limiter for preventing an increase in the dispersion of a torque threshold value at which slide occurs in the torque limiter due to the ambient environment of the torque limiter while avoiding the complication of the structure.SOLUTION: A tolerance ring 22, a rotary shaft recessed part 161a, and a lug plate 24 constitute a torque limiter 42. The tolerance ring 22, the rotary shaft recessed part 161a, and the lug plate 24 are all provided in a compressor case 20. This means the torque limiter 42 is provided in the compressor case 20. Thus, the torque limiter 42 is avoided from being exposed to an easy-to-corrode or dusty environment. This can prevent an increase in the dispersion of limiter operation torque TL due to the ambient environment of the torque limiter 42.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a compressor for compressing a fluid.

  Patent Document 1 describes a power transmission device for transmitting power from a drive source to a compressor. The power transmission has a tolerance ring provided in the power transmission path between the pulley and the shaft of the compressor. The tolerance ring is press-fitted between the two metal members while being compressed in the thickness direction. The tolerance ring is in frictional contact with the two metal members while exerting a pressing force in the radial direction, and power is transmitted by the frictional contact.

  Then, when an excessive torque is applied to the power transmission device, the frictional contact surface of the tolerance ring slips on one of the two metal members to cut off the power transmission. Thus, the power transmission device of Patent Document 1 has a function as a torque limiter.

Unexamined-Japanese-Patent No. 2002-235661

  In Patent Document 1, the torque limiter of Patent Document 1, which utilizes frictional contact, has a limiter operating torque as a torque threshold at which slippage occurs in the torque limiter, as compared to a fracture type torque limiter in which parts are broken in the middle of the power transmission path. Variation is small. This is because the limiter operating torque of the torque limiter of Patent Document 1 is not affected by a material defect or the like.

  However, in the torque limiter provided in the power transmission device of Patent Document 1, the press-fit portion into which the tolerance ring is press-fitted is exposed to the outside. Therefore, it is considered that foreign matter easily intrudes or accumulates in the press-in portion, and corrosion of the press-in portion due to water or the like also easily progresses. Therefore, in the torque limiter of Patent Document 1, it is thought that the variation in limiter operating torque is likely to be expanded due to environmental factors around the torque limiter, and the variation in limiter operating torque may rather be larger than that in the break type.

  Also, in order to avoid the influence of environmental factors around the torque limiter, apply grease and provide a sealing material such as a seal of grease sealed bearing, for example, to prevent corrosion of the press-fit part of the tolerance ring. Is assumed. However, such application of grease and sealing material is not preferable because it complicates the structure of the torque limiter and leads to an increase in size of a device including the torque limiter. As a result of the inventor's detailed examination, the above was found out.

  In view of the above-described points, in the compressor provided with the torque limiter, in the present invention, the variation of the torque threshold at which the slip occurs in the torque limiter is increased due to the surrounding environment of the torque limiter while avoiding complication of the structure. To prevent that.

In order to achieve the above object, the compressor according to claim 1 is
A compressor case (20) constituting an outer shell of the compressor;
A compression mechanism (40) for compressing the fluid;
A torque limiter (42) provided in a power transmission path for transmitting power to the compression mechanism and generating slippage when the transmission torque transmitted to the compression mechanism becomes equal to or greater than a predetermined torque threshold value;
The torque limiter is provided in the compressor case.

  This can prevent the torque limiter from being exposed to a corrosive environment or a dusty environment. Therefore, it is possible to prevent the variation in the torque threshold from becoming large due to the surrounding environment of the torque limiter.

  In addition, since a configuration such as application of grease or addition of a seal material is not required for the torque limiter, it is possible to avoid the complication of the structure.

  In addition, each code | symbol in the parentheses described in the claim and this column is an example which shows the correspondence with the specific content as described in embodiment mentioned later.

It is a schematic block diagram of the refrigerating-cycle apparatus provided with the compressor of 1st Embodiment. It is the fragmentary sectional view which carried out cross-sectional illustration of the principal part of the compressor of 1st Embodiment. FIG. 3 is a partially enlarged view of a portion III of FIG. 2; It is the perspective view which showed the general | schematic shape of the tolerance ring which the compressor of 1st Embodiment has. It is the fragmentary sectional view which carried out cross-sectional illustration of the principal part of the compressor of 2nd Embodiment, Comprising: It is a figure corresponded in FIG. It is the elements on larger scale which expanded and showed the VI part of FIG.

  Hereinafter, each embodiment will be described with reference to the drawings. In the following embodiments, parts identical or equivalent to each other are denoted by the same reference numerals in the drawings.

First Embodiment
As shown in FIG. 1 and FIG. 2, the compressor 16 of the present embodiment is a compressor for air conditioning, and is rotationally driven by power from an engine 12 which is a drive source. The power of the engine 12 is transmitted to the rotation shaft 161 of the compressor 16 via the pulley 121 of the engine 12, the drive belt 18 and the electromagnetic clutch 19 in order. The drive belt 18 is wound around a pulley 121 of the engine 12 and a pulley 191 of the electromagnetic clutch 19.

  As shown in FIG. 2, the rotation shaft 161 of the compressor 16 rotates around the compressor axis CL as a predetermined axis. And in this embodiment, axial direction DRa of the rotating shaft 161 of the compressor 16, ie, axial direction DRa of compressor axial center CL, is called compressor axial direction DRa. Further, the radial direction DRr of the rotary shaft 161, that is, the radial direction DRr of the compressor axial center CL is referred to as a compressor radial direction DRr.

  As shown in FIG. 1, the compressor 16 constitutes a part of the refrigeration cycle apparatus 14 in which the refrigerant circulates, compresses the refrigerant, and discharges the refrigerant after compression. The refrigeration cycle apparatus 14 is for air conditioning of a passenger compartment, and includes, in addition to the compressor 16, a condenser 141, an expansion valve 142, an evaporator 143, and the like. In the refrigeration cycle apparatus 14, the compressor 16, the condenser 141, the expansion valve 142, and the evaporator 143 are connected to form an annular refrigerant circuit. Therefore, the refrigerant discharged from the compressor 16 flows in the order of the condenser 141, the expansion valve 142, and the evaporator 143, and the refrigerant flowing out of the evaporator 143 is sucked into the compressor 16.

  As shown in FIG. 2, the electromagnetic clutch 19 includes a pulley 191, a stator 193, an electromagnetic coil 194, an armature 195, a damper 196, and an inner hub 197. The electromagnetic clutch 19 connects or disconnects the pulley 191 and the armature 195 to interrupt power transmission from the engine 12 to the compressor 16. 2 shows the pulley 191 and the armature 195 separated from each other. The same applies to later-described drawings for displaying the electromagnetic clutch 19 unless otherwise specified.

  The pulley 191 of the electromagnetic clutch 19 is rotatably supported by a bearing 192 around the compressor axis CL, and a drive belt 18 is wound around the outer periphery of the pulley 191.

  The stator 193 of the electromagnetic clutch 19 is formed annularly around the compressor axis CL. The electromagnetic coil 194 is accommodated in its stator 193. The stator 193 is a non-rotating member that does not rotate.

  The stator 193 and the armature 195 are made of a magnetic material such as iron. The armature 195 is a disk-shaped member which spreads in the compressor radial direction DRr. The armature 195 and the stator 193 are arranged side by side in the compressor axial direction DRa with a part of the pulley 191 interposed therebetween. The stator 193 forms a slight gap with the pulley 191 so as not to interfere with the pulley 191.

  The damper 196 is configured to include an elastic body having elasticity. The radially outer end of the damper 196 is fixed to the armature 195, and the radially inner end of the damper 196 is fixed to the inner hub 197. Further, the inner hub 197 is non-rotatably coupled to the rotation shaft 161 of the compressor 16 by, for example, spline fitting. Therefore, the armature 195, the damper 196, the inner hub 197, and the rotating shaft 161 integrally rotate around the compressor axis CL.

  When the electromagnetic coil 194 is energized, the armature 195 is attracted to the side of the stator 193 by the magnetic force of the electromagnetic coil 194, so that the armature 195 is in close contact with the pulley 191. Thereby, power transmission from the pulley 191 to the rotating shaft 161 of the compressor 16 becomes possible.

  On the other hand, when the energization of the electromagnetic coil 194 is cut off, that is, when the electromagnetic coil 194 is not energized, the above-described magnetic force is not generated. Therefore, the armature 195 is separated from the pulley 191 by the elastic force of the elastic body of the damper 196. Thereby, the power transmission from the pulley 191 to the rotating shaft 161 is shut off. That is, power transmission from the engine 12 to the compressor 16 is shut off.

  As shown in FIG. 2, the compressor 16 of the present embodiment is a variable displacement swash plate compressor. The compressor 16 includes a rotary shaft 161, a compressor case 20, a tolerance ring 22, a lug plate 24, a thrust bearing 26, a swash plate 28, a plurality of pistons 30, a plurality of shoes 32, a suction valve 34 and a discharge valve 36. ing.

  The compressor case 20 is composed of a plurality of parts. Specifically, the compressor case 20 includes a first case portion 201, a second case portion 202, a case lid portion 203, and a plate 204. The compressor case 20 accommodates therein the tolerance ring 22, the lug plate 24, the thrust bearing 26, the swash plate 28, the plurality of pistons 30, and the plurality of shoes 32. In short, the compressor case 20 constitutes the outer shell of the compressor 16.

  The refrigerant mixed with the refrigeration oil Fo is introduced into the internal space of the compressor case 20 accommodating the tolerance ring 22 and the lug plate 24 and the like. FIG. 2 shows that a part of the refrigeration oil Fo separated from the refrigerant is accumulated below the internal space of the compressor case 20. As shown in FIG.

  The rotation shaft 161 of the compressor 16 is supported by the compressor case 20 so as to be rotatable around the compressor axis CL. And, the rotary shaft 161 is also provided in the compressor case 20, and at the same time, it protrudes from the compressor case 20 to one side of the compressor axial direction DRa, and the inner hub 197 is fitted in the protruding portion It is correct.

  The first case portion 201 constitutes a part of the outer shell of the compressor 16, and inside the first case portion 201, a plurality of compression chambers 201a for compressing the refrigerant are formed. Therefore, the first case portion 201 includes the cylinder 201b in which the compression chamber 201a is formed.

  The second case portion 202 is connected to one side of the first case portion 201 in the compressor axial direction DRa. The case lid portion 203 is connected to the other side of the first case portion 201 in the compressor axial direction DRa. The case lid portion 203 covers the other side of the first case portion 201 in the compressor axial direction DRa with the plate 204 interposed between the case lid portion 203 and the first case portion 201.

  As shown in FIGS. 2 and 3, the lug plate 24 has an inner circumferential portion 241 which constitutes an inner circumferential portion of the lug plate 24. Inside the inner peripheral portion 241, a plate through hole 241a is formed which penetrates the inner peripheral portion 241 in the compressor axial direction DRa.

  The rotary shaft 161 of the compressor 16 is inserted through the plate through hole 241 a, and the lug plate 24 is supported by the rotary shaft 161 in the compressor radial direction DRr via the tolerance ring 22.

  Further, the rotation shaft 161 has a portion inserted into the plate through hole 241a as a rotation shaft recess 161a. The rotary shaft recess 161 a is disposed in the compressor case 20. The rotary shaft recess 161 a is recessed inward in the compressor radial direction DRr and formed annularly around the compressor axis CL. The rotary shaft recess 161a has a recess bottom surface 161b that forms the bottom of the rotary shaft recess 161a, and the recess bottom surface 161b faces the outside in the compressor radial direction DRr.

  Further, the inner circumferential portion 241 of the lug plate 24 has a plate inner circumferential surface 241 b formed inside the inner circumferential portion 241 and in contact with the tolerance ring 22. The plate inner circumferential surface 241b faces inward in the compressor radial direction DRr.

  Further, the inner circumferential portion 241 has an inner circumferential convex portion 241 c disposed at one end of the compressor axial direction DRa. The inner circumferential convex portion 241c is disposed on one side of the plate inner circumferential surface 241b in the compressor axial direction DRa, and protrudes inward with respect to the plate inner circumferential surface 241b in the compressor radial direction DRr. Therefore, the inner peripheral convex portion 241c has an inner peripheral step portion 241d forming a step in the compressor radial direction DRr at the other end of the inner peripheral convex portion 241c in the compressor axial direction DRa.

  The lug plate 24 also has an axial support portion 242 provided radially outward of the inner circumferential portion 241. The lug plate 24 is supported by the axial support portion 242 by the thrust bearing 26 from one side of the compressor axial direction DRa. The thrust bearing 26 is disposed between the axial support portion 242 of the lug plate 24 and the inner wall surface of the second case portion 202.

  In detail, the thrust bearing 26 prevents the lug plate 24 from being displaced relative to the compressor case 20 to one side in the compressor axial direction DRa. Further, the tolerance ring 22 is prevented from being displaced to one side in the compressor axial direction DRa with respect to the compressor case 20 by the inner peripheral convex portion 241 c of the lug plate 24. In addition, the ring base 223 of the tolerance ring 22 prevents the rotational shaft 161 from being displaced relative to the compressor case 20 to one side in the compressor axial direction DRa. Furthermore, the rotation shaft 161 is provided so as not to be displaced to the other side of the compressor axial direction DRa with respect to the compressor case 20. Accordingly, the thrust bearing 26 prevents the lug plate 24 from being displaced relative to the rotary shaft 161 to one side in the compressor axial direction DRa.

  As shown in FIGS. 3 and 4, the tolerance ring 22 is a ring member extending annularly around the compressor axis CL (see FIG. 2), and is formed in a thin plate shape with the compressor radial direction DRr in the thickness direction. ing. The tolerance ring 22 is a leaf spring member that exerts an urging force in the compressor radial direction DRr that repels the elastic deformation whose thickness is compressed.

  The tolerance ring 22 exerts a frictional force on each of the rotation shaft 161 and the lug plate 24 by the elastic deformation of the tolerance ring 22. The frictional force causes the tolerance ring 22 to transmit the rotation of the rotating shaft 161 to the lug plate 24. That is, the lug plate 24 is not directly restrained in the circumferential direction with respect to the rotation shaft 161, and the friction force exerted by the tolerance ring 22 makes the lug plate 24 together with the tolerance ring 22 and the rotation shaft 161 Rotate around CL. The detailed configuration of the tolerance ring 22 will be described later.

  As shown in FIG. 2, since the compressor 16 is a device that compresses a refrigerant that is a fluid, the compressor 16 includes a compression mechanism unit 40 that compresses the refrigerant. The compression mechanism portion 40 has a swash plate 28, a piston 30, and a shoe 32 as main components. The compression mechanism unit 40 is provided in the compressor case 20.

  Specifically, the swash plate 28 is engaged with the lug plate 24 so as to rotate around the compressor axis CL with the lug plate 24. The peripheral portion of the swash plate 28 is connected to the piston 30 via the shoe 32. Therefore, the rotation of the lug plate 24 is converted to the reciprocating motion of the piston 30 along the compressor axial direction DRa by passing through the swash plate 28 and the shoes 32.

  When the piston 30 reciprocates, the volume of the compression chamber 201 a formed by the piston 30 and the cylinder 201 b increases or decreases with the reciprocation. On the other side of the compression chamber 201a in the compressor axial direction DRa, that is, on the side opposite to the piston 30, the suction valve 34 and the discharge valve 36, which are on-off valves, are provided for each compression chamber 201a. The suction port 204a and the discharge port 204b are formed.

  Then, when the suction valve 34 is opened as the piston 30 reciprocates, the refrigerant flows from the suction chamber 203a formed in the case cover 203 through the suction port 204a into the compression chamber 201a. Further, when the discharge valve 36 is opened with the reciprocation of the piston 30, the compressed refrigerant flows from the compression chamber 201a through the discharge port 204b to the discharge chamber 203b formed in the case lid 203. The high-pressure refrigerant flowing to the discharge chamber 203 b is discharged from the discharge chamber 203 b to the outside of the compressor 16. Thus, the compression mechanism unit 40 compresses the refrigerant and discharges the compressed refrigerant. The discharged refrigerant flows from the compressor 16 to the condenser 141 of FIG. 1 in this embodiment.

  Next, the detailed configuration of the tolerance ring 22 will be described. As shown in FIGS. 3 and 4, the tolerance ring 22 is not a completely closed annular shape, but has one circumferential end 221 and the other circumferential end 222, and the circumferential end 221 and the other circumferential end A space 22 a is formed between the space 222 and the space 222.

  Specifically, the tolerance ring 22 has a band-like ring base 223 extending in the circumferential direction of the rotation shaft 161, and a plurality of ring projections 224 projecting outward from the ring base 223 in the radial direction DRr of the compressor. . Each of the plurality of ring protrusions 224 has a shape extending in the compressor axial direction DRa. Further, the plurality of ring protrusions 224 are arranged at an interval in the circumferential direction centering on the compressor axial center CL. The plurality of ring projections 224 are configured as elastic portions that can be elastically compressed in the thickness direction of the tolerance ring 22, that is, the compressor radial direction DRr. In FIG. 4, the illustration of the back side shape of the ring projection 224 appearing on the inner side in the radial direction of the tolerance ring 22 is omitted.

  As shown in FIGS. 3 and 4, the tolerance ring 22 is wound around the rotary shaft recess 161a and fitted into the rotary shaft recess 161a. That is, the tolerance ring 22 is disposed between the concave bottom surface 161 b of the rotating shaft 161 and the plate inner circumferential surface 241 b of the lug plate 24. The tolerance ring 22 is press-fitted between the recess bottom surface 161 b and the plate inner peripheral surface 241 b. Specifically, the tolerance ring 22 is sandwiched between the concave bottom surface 161b and the plate inner circumferential surface 241b in the compressor radial direction DRr, whereby the plurality of ring projections 224 are compressed and deformed in the compressor radial direction DRr. It is done.

  Therefore, the tolerance ring 22 functions as a pressing member that exerts a pressing force due to the compressive deformation of the ring projection 224. That is, the tolerance ring 22 presses the tip end surface 224a of the ring protrusion 224 and the plate inner circumferential surface 241b opposite to the tip end surface 224a in the compressor radial direction DRr. At the same time, the tolerance ring 22 presses the inner circumferential surface 223a of the ring base 223 and the concave bottom surface 161b of the rotary shaft 161 opposite to the inner circumferential surface 223a against each other in the compressor radial direction DRr.

  In addition, since the tip end surface 224a of the ring protrusion portion 224 is opposed to the plate inner peripheral surface 241b, it is a surface facing the outside in the compressor radial direction DRr. On the other hand, since the inner peripheral surface 223a of the ring base 223 is opposed to the concave bottom surface 161b of the rotary shaft 161, the inner peripheral surface 223a faces inward in the compressor radial direction DRr.

  From such a configuration, as shown in FIG. 2 and FIG. 3, when the electromagnetic coil 194 is energized, the power of the engine 12 is the drive belt 18, the electromagnetic clutch 19, the rotating shaft 161, the tolerance ring 22, the lug plate 24, and the compression. It is transmitted in order of the mechanism unit 40. That is, in the compressor 16, the rotating shaft 161, the tolerance ring 22, and the lug plate 24 are provided in the power transmission path for transmitting the power of the engine 12 from the electromagnetic clutch 19 to the compression mechanism 40.

  The tolerance ring 22, the rotary shaft recess 161a, and the lug plate 24 functionally constitute a torque limiter 42 for transmitting power by frictional force. Specifically, the torque limiter 42 is configured to provide friction between the tip end surface 224 a of the ring protrusion 224 and the plate inner peripheral surface 241 b and between the inner peripheral surface 223 a of the ring base 223 and the concave bottom surface 161 b of the rotary shaft 161. Power is transmitted by friction.

  Further, from the functional viewpoint of the configuration of the torque limiter 42, the torque limiter 42 received from the drive portion 42a provided in the power transmission path to the compression mechanism portion 40 and from the drive portion 42a provided in the power transmission path And a driven portion 42 b for transmitting power to the compression mechanism portion 40. The drive portion 42a and the driven portion 42b rotate around the compressor axis CL. The drive portion 42a includes the rotary shaft recess 161a, and the driven portion 42b includes the lug plate 24.

  The torque limiter 42 of the present embodiment performs power transmission by the frictional force as described above. Therefore, when the transmission torque Tr transmitted to the compression mechanism section 40 becomes equal to or greater than the predetermined torque threshold TL, the torque limiter 42 Slippage occurs. In short, when the excessive transmission torque Tr is applied to the torque limiter 42, slippage occurs in the torque limiter 42.

  When slippage occurs in the torque limiter 42, relative rotation occurs between the rotary shaft recess 161a and the tolerance ring 22, or between the inner circumferential portion 241 of the lug plate 24 and the tolerance ring 22, and power transmission is limited. Be done. For example, when the slip occurs, the rotation shaft 161 of the compressor 16 is rotated while the rotation of the lug plate 24 is stopped.

  Further, since the frictional force for the torque limiter 42 to transmit power is exerted according to the pressing force of the tolerance ring 22, the limiter operating torque TL, which is the torque threshold TL, increases as the pressing force of the tolerance ring 22 increases. Become. Therefore, the limiter operating torque TL is preset according to the amount of elastic compression deformation of the tolerance ring 22 and the spring constant.

  For example, the amount of elastic compression deformation and the spring constant of the tolerance ring 22 are set such that the limiter operating torque TL is always smaller than the belt slip torque at which the drive belt 18 slips relative to the pulley 191. This is to prevent the drive belt 18 from slipping on the pulley 191.

  Furthermore, the amount of elastic compression deformation and the spring constant of the tolerance ring 22 are also set so that the limiter operating torque TL is always larger than the steady state transmission torque which is the steady state transfer torque Tr during the operation of the compressor 16. ing. The frequent occurrence of the slippage of the torque limiter 42 substantially impairs the operation of the compressor 16.

  Here, the tolerance ring 22 is in frictional contact with both the inner circumferential portion 241 of the lug plate 24 and the rotary shaft recess 161 a. Therefore, when slippage occurs in the torque limiter 42, the tolerance ring 22 slides against one of the inner circumferential portion 241 of the lug plate 24 and the rotary shaft recess 161a, and relative rotation with respect to the other. It will not do. That is, in the first case where the tolerance ring 22 is fixed relative to the rotation shaft 161 while being fixed relative to the lug plate 24, the tolerance ring 22 rotates relative to the lug plate 24 while fixed relative to the rotation shaft 161. There is also a second case.

  For example, in the first and second cases described above, it is assumed that the tolerance ring 22 is fixed to the lug plate 24 and rotates relative to the rotation shaft 161. In that case, since the tolerance ring 22 is fixed to the lug plate 24, the tolerance ring 22 is also included in the driven portion 42b of the torque limiter 42 including the lug plate 24. The recessed bottom surface 161b of the rotating shaft 161 is the drive-side friction surface formed on the drive portion 42a, and the inner peripheral surface 223a of the ring base 223 is formed on the driven portion 42b and pressed against the drive-side friction surface Become the driven side friction surface.

  Therefore, in the first case, the slippage of the torque limiter 42 specifically refers to the circumferential direction of the rotary shaft 161 with respect to the inner peripheral surface 223a as the driven side friction surface as the concave bottom surface 161b as the drive side friction surface. To slide on. In short, the slip of the torque limiter 42 means that the drive portion 42a rotates relative to the driven portion 42b.

  Furthermore, the rotation shaft recess 161a is a recess that configures a part of the drive portion 42a, and the ring base 223 is a fitting portion that configures a portion of the driven portion 42b and is fitted into the rotation shaft recess 161a. In the first case, the ring base 223 and the rotation shaft recess 161a function as a displacement prevention unit that prevents displacement of the drive unit 42a and the driven unit 42b in the compressor axial direction DRa.

  In other words, in this case, the torque limiter 42 includes the ring base 223 and the rotary shaft recess 161 a as a positional deviation prevention unit. Then, when the concave bottom surface 161b of the rotary shaft 161 slides with respect to the inner circumferential surface 223a of the ring base 223, the rotary shaft concave portion 161a restrains the ring base 223 in the compressor axial direction DRa. Thus, the displacement prevention unit prevents the drive portion 42a from being displaced with respect to the driven portion 42b in the compressor axial direction DRa.

  Conversely, a second case is assumed where the tolerance ring 22 is fixed relative to the rotation shaft 161 and rotates relative to the lug plate 24. In that case, since the tolerance ring 22 is fixed to the rotation shaft recess 161a of the rotation shaft 161, the tolerance ring 22 is also included in the drive portion 42a of the torque limiter 42 including the rotation shaft recess 161a. Become. Then, the tip end surface 224a of the ring projection portion 224 becomes a drive-side friction surface formed in the drive portion 42a, and the plate inner peripheral surface 241b is formed in the driven portion 42b and is pressed against the drive-side friction surface. It becomes the drive side friction surface.

  Therefore, in the second case, the slip of the torque limiter 42 specifically means that the tip end surface 224a as the drive side friction surface is the circumference of the rotary shaft 161 with respect to the plate inner peripheral surface 241b as the driven side friction surface. It is sliding in the direction. In short, the slip of the torque limiter 42 means that the drive portion 42a rotates relative to the driven portion 42b, as in the first case.

  Further, the one-side protrusion forming portion 224b formed on one side of the ring protrusion portion 224 in the compressor axial direction DRa constitutes a part of the driving portion 42a to form a step in the compressor radial direction DRr, and a lug plate It is engaged with the inner circumferential step portion 241 d. That is, in the second case, the one side protrusion forming portion 224b is a driving side step portion engaged with the inner peripheral step portion 241d as the driven side step portion.

  Then, when the tip end surface 224a of the ring protrusion 224 slides on the plate inner circumferential surface 241b, in the thrust bearing 26, the driven portion 42b is displaced to one side in the compressor axial direction DRa with respect to the driving portion 42a. To prevent. At the same time, the one side projection forming portion 224b of the tolerance ring 22 has the inner circumferential step portion 241d of the lug plate 24 so as to prevent the driven portion 42b from shifting to the other side in the compressor axial direction DRa with respect to the driving portion 42a. Lock it.

  In the second case, in this manner, the driven portion 42b of the torque limiter 42 is prevented from being displaced relative to the drive portion 42a in the compressor axial direction DRa. That is, the one-side protrusion forming portion 224b of the tolerance ring 22, the inner circumferential step portion 241d of the lug plate 24, and the thrust bearing 26 function as the above-described positional deviation preventing portion. In other words, in this case, the torque limiter 42 has the one-side protrusion forming portion 224 b, the inner circumferential step portion 241 d, and the thrust bearing 26 as the positional deviation preventing portion.

  As described above, according to the present embodiment, as shown in FIG. 2 and FIG. 3, the tolerance ring 22, the rotary shaft recess 161 a and the lug plate 24 constitute the torque limiter 42. The tolerance ring 22, the rotary shaft recess 161 a and the lug plate 24 are all provided in the compressor case 20. That is, the torque limiter 42 is provided in the compressor case 20.

  This can prevent the torque limiter 42 from being exposed to a corrosive environment or a dusty environment. Therefore, it is possible to prevent the variation of the limiter operating torque TL from becoming large due to the ambient environment of the torque limiter 42.

  For example, in the present embodiment, the torque limiter 42 is disposed in a space common to the compression mechanism unit 40 in the compressor case 20. Therefore, it is possible to protect the torque limiter 42 by using the internal space of the compressor case 20 prepared to avoid the exposure of the compression mechanism 40 to an environment susceptible to corrosion and a dusty environment. It is.

  In addition, since the torque limiter 42 is not required to have a configuration such as application of grease or addition of a sealing material, it is possible to avoid complication of the structure.

  Particularly in the present embodiment, the contact portion of the tolerance ring 22 with respect to the rotary shaft recess 161 a and the inner circumferential portion 241 of the lug plate 24 is disposed in the compressor case 20, that is, in the internal space of the compressor case 20. Then, since the refrigerant mixed with the refrigerator oil Fo is introduced into the internal space of the compressor case 20, the contact portion of the tolerance ring 22 is placed in an atmosphere containing the refrigerant and the refrigerator oil Fo. Furthermore, the temperature environment is also stabilized in the compressor case 20, and normally, it is expected that splash lubrication of the refrigerator oil Fo can be expected. From these things, as compared with the case where the torque limiter 42 is provided outside the compressor case 20, in the present embodiment, it is possible to reduce the variation and the temporal change of the limiter operating torque TL.

  Further, according to the present embodiment, when the transmission torque Tr transmitted to the compression mechanism portion 40 becomes equal to or more than the predetermined limiter operating torque TL, in short, when an excessive transmission torque Tr is applied to the torque limiter 42. Causes the torque limiter 42 to slip.

  For example, as a case where the excessive transmission torque Tr is added, there may be a case where the compressor 16 breaks down. Specifically, as a failure of the compressor 16, when the lug plate 24 can not rotate due to seizing between the swash plate 28 and the shoe 32 in a severe sliding condition or between the piston 30 and the cylinder 201b. That is, the compressor 16 is often in a locked state. When the compressor 16 is in the locked state, a torque (that is, an excessive transmission torque Tr) much larger than the normal operating torque is applied between the lug plate 24 and the rotation shaft 161 of the compressor 16. Therefore, when the compressor 16 is in the locked state, slippage occurs in the torque limiter 42 between the rotary shaft recess 161a and the tolerance ring 22 or between the inner circumferential portion 241 of the lug plate 24 and the tolerance ring 22. Do.

  Due to the occurrence of this slippage, a torque exceeding the limiter operating torque TL is applied to the fastening portion between the rotary shaft 161 and the inner hub 197 of the electromagnetic clutch 19 and the frictional contact portion between the armature 195 of the electromagnetic clutch 19 and the friction surface of the pulley 191 It does not join. Then, no torque exceeding the limiter operating torque TL is applied to the portion of the pulley 191 of the electromagnetic clutch 19 around which the drive belt 18 is wound. Therefore, it is possible to prevent serious situations such as breakage of the fastening portion between the rotating shaft 161 and the inner hub 197, burning of the frictional contact portion between the armature 195 and the friction surface of the pulley 191 and melting of the drive belt 18. It is.

  Further, the lug plate 24 and the rotating shaft 161, into which the tolerance ring 22 is press-fitted, are existing parts necessary for the compressor 16 even if the torque limiter 42 is not provided. Therefore, the increase in the number of parts resulting from the provision of the torque limiter 42 can be suppressed, and the addition of special heat treatment or processing is hardly necessary. By the way, there is no need to apply grease or add a seal, which is required when installing a torque limiter outside the compressor 16. In short, in the present embodiment, since the torque limiter 42 is provided in the compressor case 20, stable limiter operating torque TL can be obtained over a long period of time without increasing the size of the compressor 16 at low cost. it can.

  Further, according to the present embodiment, as shown in FIGS. 2 and 3, the torque limiter 42 includes the drive portion 42 a provided in the power transmission path for transmitting the power of the engine 12 to the compression mechanism portion 40. There is. At the same time, the torque limiter 42 includes a driven portion 42 b provided in the power transmission path and transmitting the power received from the drive portion 42 a to the compression mechanism 40. The drive-side friction surface is formed in the drive portion 42a, and the driven-side friction surface pressed against the drive-side friction surface is formed in the driven portion 42b, and the torque limiter 42 Power is transmitted by friction with the driven side friction surface. The slip of the torque limiter 42 means that the drive-side friction surface slides against the driven-side friction surface, and the drive portion 42 a rotates relative to the driven portion 42 b.

  Therefore, the friction force between the drive-side friction surface and the driven-side friction surface is increased or decreased by adjusting the pressing force pressing the driven-side friction surface against the drive-side friction surface. It is possible to easily adjust the TL. In the case where the tolerance ring 22 is included in the driven portion 42b, the concave bottom surface 161b of the rotating shaft 161 is the driving side friction surface, and the inner circumferential surface 223a of the ring base 223 is the driven side friction surface. On the other hand, when the tolerance ring 22 is included in the drive portion 42a, the tip end surface 224a of the ring protrusion 224 becomes the drive side friction surface, and the plate inner peripheral surface 241b of the lug plate 24 becomes the driven side friction surface. Become.

  Further, according to the present embodiment, as shown in FIG. 2 and FIG. 3, when the drive side friction surface slides against the driven side friction surface, as shown in FIG. 2 and FIG. With respect to the portion 42b, the displacement in the compressor axial direction DRa is prevented. Therefore, it is possible to prevent the driven portion 42b from falling off from the driving portion 42a due to the positional deviation between the driven portion 42b and the driving portion 42a in the compressor axial direction DRa. When the tolerance ring 22 is included in the driven portion 42b, the ring base 223 and the rotation shaft recess 161a function as a positional deviation prevention unit. On the other hand, when the tolerance ring 22 is included in the drive portion 42a, the one-side projection forming portion 224b of the tolerance ring 22, the inner circumferential step portion 241d of the lug plate 24, and the thrust bearing 26 function as a positional deviation prevention portion Do.

  Further, according to the present embodiment, when the tolerance ring 22 is included in the driven portion 42b, the displacement prevention portion is fitted into the rotary shaft recess 161a recessed in the compressor radial direction DRr and the rotary shaft recess 161a. And a ring base 223, which is a wedge insertion part. The rotary shaft recess 161a constitutes a part of the drive part 42a, and the ring base 223 constitutes a part of the driven part 42b. The positional deviation prevention unit prevents the drive portion 42a from being displaced relative to the driven portion 42b in the compressor axial direction DRa by the rotary shaft concave portion 161a constraining the ring base 223 in the compressor axial direction DRa. Therefore, it is possible to prevent positional deviation between the driven portion 42b and the drive portion 42a in the compressor axial direction DRa with a simple configuration.

  Further, according to the present embodiment, when the tolerance ring 22 is included in the drive unit 42a, the displacement prevention unit forms a part of the drive unit 42a and forms a step on the one side that forms a step in the compressor radial direction DRr. A portion 224b. At the same time, the position shift prevention portion has an inner circumferential step portion 241 d which constitutes a part of the driven portion 42 b and forms a step in the compressor radial direction DRr, and a thrust bearing 26. The thrust bearing 26 prevents the driven portion 42b from shifting to one side of the drive shaft direction DRa with respect to the drive portion 42a. The one side protrusion forming portion 224b locks the inner circumferential step portion 241d so as to prevent the driven portion 42b from shifting to the other side in the compressor axial direction DRa with respect to the driving portion 42a. Therefore, it is possible to prevent the positional deviation between the driven portion 42b and the drive portion 42a in the compressor axial direction DRa with a simple configuration while using the thrust bearing 26.

  Further, according to the present embodiment, when the tolerance ring 22 is fixed relative to the lug plate 24 and rotates relative to the rotation shaft 161, the driven portion 42b of the torque limiter 42 functions as a pressing member. Having 22. The inner peripheral surface 223a of the ring base 223 of the tolerance ring 22 is the above-mentioned driven side friction surface. Therefore, it is not necessary to provide a member having the driven side friction surface separately from the tolerance ring 22. Therefore, it is easy to reduce the number of parts of the torque limiter 42 and to miniaturize the torque limiter 42.

  On the other hand, when the tolerance ring 22 is fixed relative to the rotation shaft 161 and rotates relative to the lug plate 24, the drive portion 42 a of the torque limiter 42 has the tolerance ring 22. Then, the tip end surface 224a of the ring protrusion portion 224 of the tolerance ring 22 becomes the drive side friction surface. Therefore, it is not necessary to provide a member having the drive side friction surface separately from the tolerance ring 22. Therefore, it is easy to reduce the number of parts of the torque limiter 42 and to miniaturize the torque limiter 42.

Second Embodiment
Next, a second embodiment will be described. In the present embodiment, points different from the first embodiment described above will be mainly described. In addition, the same or equivalent parts as those of the above-described embodiment will be described by omitting or simplifying them. The same applies to the description of the embodiments described later.

  As shown in FIGS. 5 and 6, in the compressor 16 of this embodiment, the torque limiter 42 is provided in the power transmission path for transmitting the power of the engine 12 to the compression mechanism 40 as in the first embodiment described above. And rotates around the compressor axis CL.

  However, in the torque limiter 42 of the present embodiment, a configuration in which a part of the lug plate 24 is sandwiched by the two friction members 44 and 46 in the compressor axial direction DRa is employed. The present embodiment is different from the first embodiment in this point.

  Specifically, the lug plate 24 has an inner circumferential portion 243 that constitutes an inner circumferential portion of the lug plate 24. Inside the inner circumferential portion 243, a plate through hole 243a into which the rotary shaft 161 of the compressor 16 is inserted is formed. The inner circumferential portion 243 of the lug plate 24 is also a part of the torque limiter 42.

  The torque limiter 42 has a first friction member 44, a second friction member 46, a disc spring 48 and a snap ring 49 in addition to the inner circumferential portion 243 of the lug plate 24. The inner circumferential portion 243, the first friction member 44, the second friction member 46, the disc spring 48, and the snap ring 49 are all provided in the compressor case 20. In short, in the present embodiment as well as the first embodiment, the torque limiter 42 is provided in the compressor case 20.

  In the present embodiment, the first friction member 44 and the second friction member 46 constitute the drive portion 42a of the torque limiter 42, and the inner circumferential portion 243 of the lug plate 24 constitutes the driven portion 42b.

  The first friction member 44 and the second friction member 46 are disk-shaped plate members whose thickness direction is the compressor axial direction DRa. The first friction member 44 and the second friction member 46 are disposed side by side in the compressor axial direction DRa so as to sandwich the inner circumferential portion 243 of the lug plate 24 therebetween. Specifically, the first friction member 44 is disposed on one side of the inner circumferential portion 243 of the lug plate 24 on the one side in the compressor axial direction DRa, and is in contact with the inner circumferential portion 243. In addition, the second friction material 46 is disposed on the other side of the compressor axial direction DRa with respect to the inner circumferential portion 243, and is in contact with the inner circumferential portion 243.

  The rotary shaft 161 has a fitting shaft portion 161d fitted to the two friction members 44 and 46, and a pair of radial directions from the fitting shaft portion 161d on one side in the compressor axial direction DRa with respect to the fitting shaft portion 161d. And a rotary shaft collar portion 161e which is projected in a shape of a circle. The fitting shaft portion 161 d is inserted into the plate through hole 243 a, and is also inserted radially inward of each of the first friction member 44 and the second friction member 46.

  The first friction member 44 and the second friction member 46 are non-rotatably connected to the fitting shaft portion 161d by spline fitting, for example. That is, the first friction member 44 and the second friction member 46 rotate around the compressor axis CL together with the fitting shaft portion 161d. On the other hand, the fitting shaft portion 161 d is disposed at a radial gap from the inner circumferential portion 243 of the lug plate 24. Therefore, in the present embodiment as well as in the first embodiment, the lug plate 24 is not directly restrained in the circumferential direction with respect to the rotating shaft 161.

  In this embodiment, when the electromagnetic coil 194 is energized, the power of the engine 12 is transmitted in the order of the drive belt 18, the electromagnetic clutch 19, the rotary shaft 161, the two friction members 44 and 46, the lug plate 24, and the compression mechanism 40 Be done. When slippage occurs in the torque limiter 42, power transmission is limited between the two friction members 44 and 46 and the lug plate 24.

  The rotary shaft collar portion 161 e is disposed on one side of the first friction member 44 in the compressor axial direction DRa and is in contact with the first friction member 44. Therefore, the rotary shaft collar portion 161e prevents the first friction member 44 from moving to one side of the rotary shaft 161 in the compressor axial direction DRa.

  The disc spring 48 is disposed on the other side of the second friction member 46 in the compressor axial direction DRa. The radially inner end of the disc spring 48 is locked by a snap ring 49 fitted in the groove of the rotary shaft 161 so as not to move to the other side of the compressor axial direction DRa. The radially outer end of the disc spring 48 is in contact with the second friction member 46.

  Furthermore, the disc spring 48 is compressed between the retaining ring 49 and the second friction member 46 in the compressor axial direction DRa. Therefore, the disc spring 48 biases the first friction member 44, the inner circumferential portion 243 of the lug plate 24, and the second friction member 46 to one side in the compressor axial direction DRa. The rotary shaft flange portion 161e opposes the compressor axial direction DRa with respect to the biasing force (in other words, pressing force) of the disc spring 48.

  The first friction member 44 and the second friction member 46 are pressed against the inner peripheral portion 243 of the lug plate 24 by the biasing force of the disc spring 48 as described above, and are in frictional contact with the inner peripheral portion 243. That is, the disc spring 48 functions as a pressing member that presses the first friction member 44 and the second friction member 46 against the inner circumferential portion 243.

  Specifically, the side surface of the inner circumferential portion 243 of the lug plate 24 that faces one side in the compressor axial direction DRa is formed as the first driven side friction surface 243b, and the side surface that faces the other side in the compressor axial direction DRa Is formed as a second driven side friction surface 243 c. Further, of the first friction material 44, the side surface facing the first driven friction surface 243b in the compressor axial direction DRa and facing the other is formed as a first drive friction surface 44a. At the same time, a side surface of the second friction member 46 that faces the second driven friction surface 243 c in the compressor axial direction DRa and is opposed thereto is formed as a second drive friction surface 46 a.

  Then, the first driven friction surface 243b is pressed against the first drive friction surface 44a by the biasing force of the disc spring 48, and the second driven friction surface 243c is pressed against the second drive friction surface 46a. There is. The torque limiter 42 is configured such that the friction between the first driven friction surface 243 b and the first drive friction surface 44 a and the friction between the second driven friction surface 243 c and the second drive friction surface 46 a. And transmit power.

  As described above, since power is transmitted by friction between a plurality of members, in the present embodiment as well as in the first embodiment, the transmission torque Tr transmitted to the compression mechanism portion 40 becomes equal to or higher than the predetermined limiter operating torque TL. In this case, slippage occurs in the torque limiter 42. In the present embodiment, the first drive-side friction surface 44 a slides in the circumferential direction of the rotary shaft 161 with respect to the first driven-side friction surface 243 b and the second drive-side friction surface 46 a in the present embodiment. Is sliding in the circumferential direction of the rotating shaft 161 with respect to the second driven side friction surface 243 c. In other words, the slip of the torque limiter 42 means that in the torque limiter 42, the first friction member 44 and the second friction member 46 rotate relative to the inner circumferential portion 243 of the lug plate 24.

  Specifically, since the first and second friction members 44 and 46 are the drive side and the lug plate 24 is the driven side, when the torque limiter 42 slips, the first and second frictions are generated. The members 44, 46 rotate faster than the lug plate 24. Alternatively, the first and second friction members 44, 46 rotate with the rotation shaft 161, but the lug plate 24 does not rotate.

  In the torque limiter 42, the limiter operating torque TL is determined according to the biasing force of the disc spring 48, and increases as the biasing force of the disc spring 48 increases. Therefore, the limiter operating torque TL is preset according to the amount of elastic deformation of the disc spring 48 and the spring constant.

  The present embodiment is the same as the first embodiment except for the above description. And in this embodiment, the effect show | played from the structure common to above-mentioned 1st Embodiment can be acquired similarly to 1st Embodiment.

(Other embodiments)
(1) In the first embodiment described above, as shown in FIG. 3, when slippage occurs in the torque limiter 42, the tolerance ring 22 is fixed to the lug plate 24 while rotating relative to the rotation shaft 161. There is the first case described above. In that case, since the recess of the displacement prevention portion of the torque limiter 42 is the rotary shaft recess 161a, it constitutes a part of the drive portion 42a, and the fitting portion of the displacement prevention portion is the ring base 223. It constitutes a part of the drive unit 42b. However, this is an example, and conversely, the concave portion of the displacement prevention portion constitutes a part of the driven portion 42b, and the fitting portion of the displacement prevention portion constitutes a portion of the drive portion 42a. No problem.

  (2) In the above-described first embodiment, the torque limiter 42 includes the positional deviation prevention part for preventing positional deviation between the drive part 42 a and the driven part 42 b in the compressor axial direction DRa. It is. For example, the torque limiter 42 may not have the displacement prevention unit, and the displacement prevention unit may be provided separately from the torque limiter 42. Alternatively, it can be assumed that there is no position shift prevention unit.

  (3) In the first embodiment described above, as shown in FIG. 2, the tolerance ring 22 is disposed between the rotation shaft 161 and the lug plate 24, but this is an example. The arrangement of the tolerance ring 22 is not limited to this, and the tolerance ring 22 may be provided in the middle of the power transmission path to the compression mechanism 40 and disposed in the compressor case 20. For example, the rotation shaft 161 may be divided into two in the compressor case 20, and the tolerance ring 22 may be disposed between them. Also, the lug plate 24 may be divided into a radially outer portion and a radially inner portion, and the tolerance ring 22 may be disposed therebetween. In short, it is sufficient that the drive side friction surface and the driven side friction surface, which mutually slide when the torque limiter 42 having the tolerance ring 22 as the main component, slips, be provided in the compressor case 20.

  (4) As shown in FIGS. 2 and 5 in the above-described embodiments, the compressor 16 is a variable displacement swash plate type compressor, but the present invention is not limited to this. It may be a machine. Moreover, the compressor 16 does not have to be a variable displacement type.

  (5) In addition, this invention can be variously deformed and implemented, without being limited to the above-mentioned embodiment. Further, in each of the above-described embodiments, it is needless to say that the elements constituting the embodiment are not necessarily essential except when clearly indicated as being essential and when it is considered to be obviously essential in principle. Yes.

  Further, in the above embodiments, when numerical values such as the number, numerical value, amount, range, etc. of constituent elements of the embodiment are mentioned, it is clearly indicated that they are particularly essential and clearly limited to a specific number in principle. It is not limited to the specific number except when it is done. Further, in the above embodiments, when referring to materials, shapes, positional relationships, etc. of constituent elements etc., unless specifically stated otherwise or in principle when limited to a specific material, shape, positional relationship, etc., etc. It is not limited to the material, the shape, the positional relationship, etc.

(Summary)
According to a first aspect shown in part or all of each of the above-described embodiments, the compressor includes a compressor case that constitutes an outer shell of the compressor. Further, the compressor is provided in a compression mechanism portion for compressing a fluid and a power transmission path for transmitting power to the compression mechanism portion, and the transmission torque transmitted to the compression mechanism portion becomes equal to or more than a predetermined torque threshold And a torque limiter that causes slippage. The torque limiter is provided in the compressor case.

  Further, according to the second aspect, the torque limiter includes a drive portion provided in the power transmission path, and a driven portion provided in the power transmission path and transmitting the power received from the drive portion to the compression mechanism portion. A drive-side friction surface is formed in the drive portion, and a driven-side friction surface pressed against the drive-side friction surface is formed in the driven portion, and the torque limiter includes the drive-side friction surface and the driven side friction surface Power is transmitted by friction between The slippage of the torque limiter means that the drive-side friction surface slides against the driven-side friction surface, and the drive portion rotates relative to the driven portion. Therefore, the friction force between the drive-side friction surface and the driven-side friction surface increases or decreases by adjusting the pressing force that presses the driven-side friction surface against the drive-side friction surface, thereby causing slippage in the torque limiter. It is possible to easily adjust the torque threshold of the transfer torque.

  Further, according to the third aspect, the drive portion and the driven portion rotate around a predetermined axis, and the drive-side friction surface and the driven-side friction surface face each other in the axial direction of the predetermined axis. .

  Further, according to the fourth aspect, the drive portion and the driven portion rotate around a predetermined axis, and the drive-side friction surface and the driven-side friction surface face each other in the radial direction of the predetermined axis. .

  Further, according to the fifth aspect, when the drive-side friction surface slides with respect to the driven-side friction surface, the displacement prevention unit causes the drive unit to move in the axial direction of the predetermined axial center with respect to the driven unit. Prevent it from shifting. Therefore, it is possible to prevent the drive unit from falling off the driven unit due to the positional deviation between the driven unit and the drive unit in the axial direction.

  Further, according to the sixth aspect, the displacement prevention portion has a recessed portion which is recessed in the radial direction, and a fitting portion which is fitted into the recessed portion. One of the concave portion and the fitting portion constitutes a part of the driving portion, and the other of the concave portion and the fitting portion constitutes a part of the driven portion. The positional displacement preventing portion prevents the drive portion from being displaced in the axial direction with respect to the driven portion by the concave portion restraining the insertion portion in the axial direction. Therefore, it is possible to prevent positional deviation between the driven portion and the driving portion in the axial direction with a simple configuration.

  Further, according to the seventh aspect, the displacement prevention portion is a step on the driving side which forms a part of the driving portion and forms a step in the radial direction, and a part of the driven portion to form a step in the radial direction. And a thrust bearing. The thrust bearing prevents the driven portion from shifting in the axial direction with respect to the driving portion. The drive-side stepped portion locks the driven-side stepped portion so as to prevent the driven portion from being displaced to the other side in the axial direction with respect to the drive portion. Therefore, it is possible to prevent the positional deviation between the driven portion and the driving portion in the axial direction with a simple configuration while using the thrust bearing.

  Further, according to the eighth aspect, the drive unit has a pressing member for pressing the driven side friction surface and the drive side friction surface to each other, and the drive side friction surface is formed on the pressing member of the drive unit. ing. Therefore, it is easy to reduce the number of parts of the torque limiter and to miniaturize the torque limiter.

  Further, according to the ninth aspect, the driven portion has a pressing member for pressing the driven side friction surface and the driving side friction surface to each other, and the driven side friction surface is a pressing member of the driven portion. Is formed. Even in this case, as in the above eighth aspect, it is easy to reduce the number of parts of the torque limiter and to miniaturize the torque limiter.

16 compressor 20 compressor case 40 compression mechanism section 42 torque limiter

Claims (9)

A compressor,
A compressor case (20) constituting an outer shell of the compressor;
A compression mechanism (40) for compressing the fluid;
And a torque limiter (42) which is provided in a power transmission path for transmitting power to the compression mechanism and which generates slip when the transmission torque transmitted to the compression mechanism exceeds a predetermined torque threshold.
The compressor, wherein the torque limiter is provided in the compressor case. The torque limiter includes a drive portion (42a) provided in the power transmission path, and a driven portion (42b) provided in the power transmission path and transmitting the power received from the drive portion to the compression mechanism portion. Have
Drive side friction surfaces (161b, 224a, 44a, 46a) are formed in the drive unit,
In the driven portion, driven side friction surfaces (223a, 241b, 243b, 243c) pressed to the drive side friction surface are formed.
The torque limiter transmits the power by friction between the drive-side friction surface and the driven-side friction surface,
2. The compression according to claim 1, wherein the slip of the torque limiter is that the drive-side friction surface slides against the driven-side friction surface, and the drive unit rotates relative to the driven unit. Machine. The drive unit and the driven unit rotate around a predetermined axis (CL),
The compressor according to claim 2, wherein the drive side friction surface (44a, 46a) and the driven side friction surface (243b, 243c) face each other in the axial direction (DRa) of the predetermined axial center. . The drive unit and the driven unit rotate around a predetermined axis (CL),
The compressor according to claim 2, wherein said drive side friction surface (161b, 224a) and said driven side friction surface (223a, 241b) face each other in the radial direction (DRr) of said predetermined axial center. . A displacement prevention unit (223, 161a, 224b, 241d, 26),
When the drive-side friction surface slides with respect to the driven-side friction surface, the displacement prevention unit shifts the drive unit in the axial direction (DRa) of the predetermined axial center with respect to the driven unit. The compressor according to claim 4, which prevents that. The displacement prevention portion (223, 161a) has a recess (161a) recessed in the radial direction, and a fitting portion (223) fitted in the recess.
One of the concave portion and the fitting portion constitutes a part of the driving portion, and the other of the concave portion and the fitting portion constitutes a part of the driven portion.
The compression according to claim 5, wherein the displacement prevention portion prevents the drive portion from being displaced in the axial direction with respect to the driven portion by the concave portion restraining the fitting portion in the axial direction. Machine. The displacement prevention portion (224b, 241d, 26) constitutes a part of the drive portion and a drive side step portion (224b) which forms a part of the drive portion and which forms the step in the radial direction, and a part of the driven portion. It has a driven side step portion (241d) forming the radial step and a thrust bearing (26).
The thrust bearing prevents the driven portion from being displaced to one side in the axial direction with respect to the driving portion,
The compressor according to claim 5, wherein the drive-side stepped portion locks the driven-side stepped portion so as to prevent the driven portion from being displaced to the other side in the axial direction with respect to the drive portion. . The drive unit includes a pressing member (22) that presses the driven friction surface (241b) and the drive friction surface (224a) with each other.
The compressor according to any one of claims 4 to 7, wherein the drive-side friction surface is formed on the pressing member of the drive unit. The driven portion includes a pressing member (22) that presses the driven friction surface (223a) and the drive friction surface (161b) with each other.
The compressor according to any one of claims 4 to 7, wherein the driven side friction surface is formed on the pressing member of the driven portion.

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