US20090047162A1 - Compressor and Power Transmission Device - Google Patents
Compressor and Power Transmission Device Download PDFInfo
- Publication number
- US20090047162A1 US20090047162A1 US11/886,896 US88689606A US2009047162A1 US 20090047162 A1 US20090047162 A1 US 20090047162A1 US 88689606 A US88689606 A US 88689606A US 2009047162 A1 US2009047162 A1 US 2009047162A1
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- United States
- Prior art keywords
- rotor
- hub
- rotation member
- rotary shaft
- shim
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
- F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
- F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
- F16D27/112—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with flat friction surfaces, e.g. discs
Definitions
- the present invention relates to a compressor and a power transmission device which are suitable for a refrigeration device using CO 2 gas as refrigerant.
- a compressor of this type has a housing, which contains a compression unit.
- the compression unit carries out a sequence of processes, starting with suction of refrigerant, followed by compression and discharge of the refrigerant.
- the compression unit is connected to a rotary shaft which drives the compression unit.
- the rotary shaft is disposed within the housing, and both end portions of the rotary shaft are rotatably supported by the housing through bearings.
- the rotary shaft has one end that is protruding from the housing. This one end is connected to a driving source through a power transmission path. Therefore, when the driving force of the driving source is transmitted through the power transmission path to the rotary shaft, the rotary shaft is rotated, and this rotation drives the compression unit.
- a power transmission device such as an electromagnetic clutch is also interposed in the power transmission path.
- the power transmission device controls the transmission of the driving force from the driving source to the compression unit.
- the compressor further includes a shaft sealing unit, namely, mechanical seal, which is set in between the rotary shaft and the housing.
- the mechanical seal is placed near the bearing that is located on the side of the one end of the rotary shaft, and seals the rotary shaft with respect to the housing.
- the mechanical seal includes a fixed seal face that surrounds the rotary shaft and a movable seal face that rotates with the rotary shaft and slides against the fixed seal face.
- the mechanical seal receives high pressure in the housing on the fixed seal face.
- Such sealing effect of the mechanical seal is generally presented by the product of fluid pressure (P) applied to the fixed and movable seal faces and peripheral velocity (V) of the movable seal face, that is, a PV value.
- CO 2 gas is used as refrigerant as mentioned above, the CO 2 gas decreases burdens on the global environment as it has smaller global warming potential than chlorofluorocarbon (CFC) that is commonly used as refrigerant.
- CFC chlorofluorocarbon
- the compressor is required to compress CO 2 into a high-pressure range where the CO 2 comes into a super critical state. For this reason, during operation of the compressor, the pressure in the housing becomes approximately seven to ten times higher than the case in which CFC is used as refrigerant.
- the peripheral velocity (V) of the movable seal face is reduced.
- the diameter of the rotary shaft may be reduced.
- this electromagnetic clutch includes a rotor located on the driving source side and an armature located on the rotary shaft side.
- the rotor and the armature must be spaced away from each other with a given gap between them when the electromagnetic clutch is in a resting state (refer to gap ⁇ disclosed in Patent Document 1 mentioned below).
- a ring-shaped shim is utilized.
- the shim is placed between the rotary shaft and the hub of the electromagnetic clutch. More specifically, one end portion of the rotary shaft is formed as a small-diameter shaft portion, which provides the rotary shaft with an annular stepped face that is opposed to the hub. When placed between the hub and the stepped face, the shim creates the gap between the rotor and the armature.
- the rotary shaft will be deficient in mechanical strength at the small-diameter shaft portion, and will be incapable of carrying out a stable transmission of the driving force, or torque transmission, from the driving source to the compression unit. This might result in a fracture of the rotary shaft.
- Patent Document 1 Unexamined Japanese Patent Publication No.
- the compressor comprises a housing; a rotary shaft rotatably supported in the housing, the rotary shaft having one end protruding from the housing; a compression unit contained in the housing, the compression unit for performing a sequence of processes, starting with suction of a working fluid, followed by compression and discharge of the working fluid, when driven by the rotary shaft; a shaft sealing unit disposed between the housing and the rotary shaft, for airtightly sealing the inside of the housing; and a power transmission device for transmitting a driving force from a driving source to the one end of the rotary shaft.
- the power transmission device includes a rotor rotatably supported by an outer surface of the housing through a bearing, for receiving the driving force from the driving source; a hub coupled to the one end of the rotary shaft, for rotating with the rotary shaft; a clutch mechanism for controlling transmission of rotational force from the rotor to the hub, the clutch mechanism including a first rotation member disposed adjacent to the rotor in relation to an axial direction of the rotary shaft, the first rotation member being capable of receiving the rotational force of the rotor and a second rotation member disposed adjacent to the hub in relation to the axial direction, the second rotation member being coupled to the hub and capable of receiving the rotational force of the first rotation member; and a shim sandwiched between the second rotation member and the hub, the shim determining a position of the first rotation member with respect to the rotor relative in the axial direction.
- the shim is placed not between the hub and the rotary shaft but between the hub and the second rotation member. Therefore, the rotary shaft is not required to be reduced in diameter due to the placement of the shim.
- the diameter of the rotary shaft can be reduced only in consideration of use of CO 2 gas as a working fluid, so that the diameter of the rotary shaft is not undesirably reduced. This makes it possible to secure durability of a shaft-sealing unit for a long term while avoiding the lack of mechanical strength in the rotary shaft, thereby significantly improving reliability of the compressor.
- the power transmission device is an electromagnetic clutch including an electromagnetic solenoid disposed within the rotor.
- the first rotation member of the clutch mechanism includes an armature for receiving the rotational force of the rotor when the electromagnetic solenoid is in an operating state and the armature is attracted to the rotor by the electromagnetic solenoid, and a spring element for urging the armature to secure a gap between the rotor and the armature in the axial direction, when the electromagnetic solenoid is in a resting state, the shim determining a size of the gap.
- the power transmission device may be a torque limiter for breaking transmission of the rotational force from the rotor to the rotary shaft when the rotary shaft comes into a locked state.
- the shim is used for position adjustment of the spring element and the rotor.
- the shim located between the hub and the second rotation member can have a larger pressure-receiving area than that of a shim located between the hub and the rotary shaft. Consequently, the shim is never buckled at the time of screw fastening for fixing the hub. Abrasion of the shim due to a tremor caused by variable load is also reduced.
- the clutch mechanism further includes a fastening element disposed in either one of the second rotation member and the hub, and a receiving element disposed in the other of the second rotation member and the hub, for receiving the fastening element to couple the second rotation member and the hub to each other.
- the shim has a bore into which the fastening element is inserted.
- the fastening element is any one of a bolt, a pin, and a protruding portion integrally formed in one or the other of the second rotation member and the hub.
- the fastening element and the receiving element easily and firmly couple the second rotation member and the hub to each other, and are greatly useful for improving the productivity of the compressor.
- the invention also provides the compressor using CO 2 gas as a working fluid and the power transmission device included in the compressor.
- FIG. 1 is a sectional view showing a part of a compressor according to a first embodiment
- FIG. 2 is a sectional exploded view showing a part of a power transmission device of FIG. 1 ;
- FIG. 3 is a front view of the power transmission device of FIG. 1 ;
- FIG. 4 is a front view of a hub of FIG. 2 ;
- FIG. 5 is a front view of a shim of FIG. 2 ;
- FIG. 6 is a sectional view showing a part of a compressor according to a second embodiment
- FIG. 7 is a sectional view showing a part of a compressor according to a third embodiment
- FIG. 8 is a front view of a power transmission device of FIG. 7 ;
- FIG. 9 is a front view of a shim of FIG. 7 ;
- FIG. 10 is a sectional view showing a modification example of a coupling structure for connecting an inner support and the hub of FIG. 2 to each other.
- FIG. 1 shows a part of a compressor according to a first embodiment.
- the compressor is contained in a refrigeration device using CO 2 as refrigerant. More specifically, the refrigeration plat is included in a vehicle air conditioning system.
- the compressor has a housing 2 .
- FIG. 1 only shows a part of the housing 2 .
- a rotary shaft 4 which is rotatably supported through bearings (not shown) with respect to the housing 2 .
- a mechanical seal 6 serving as a shaft sealing unit is also located in the housing 2 .
- the mechanical seal 6 keeps an airtight condition between the housing 2 and the rotary shaft 4 .
- the mechanical seal 6 includes a sheet 7 a fixed to the housing 2 and a seal ring 7 b fitted to the rotary shaft 4 and pressed against the sheet 7 a .
- the sheet 7 a and the seal ring 7 b have annular seal faces 8 a and 8 b that are in close contact.
- lip seals may be utilized as the shaft sealing unit.
- the lip seal is placed between the rotary shaft 4 and the housing 2 and has a cylindrical seal face.
- the rotary shaft 4 has one end portion 10 protruding from the housing 2 and the other end portion (not shown) that is positioned within the housing 2 .
- the other end portion of the rotary shaft 4 is connected to a compression unit 12 .
- the compression unit 12 is accommodated in the housing 2 and is driven by the rotary shaft 4 .
- the compression unit 12 is, for example, either one of a swash-plate compression unit including a piston that makes a reciprocating motion according to the rotary shaft 4 and a scroll compression unit including a movable scroll that makes an orbiting motion according to the rotary shaft 4 .
- the compression unit 12 When driven, the compression unit 12 repeatedly performs a sequence of processes, starting with suction of CO 2 refrigerant, followed by compression and discharge of the CO 2 refrigerant, thereby circulating the CO 2 refrigerant through a refrigerant circuit of the refrigeration device.
- the one end portion 10 of the rotary shaft 4 is connected to a driving source 15 through a power transmission path 13 .
- the driving source 15 is either an engine or motor of a vehicle.
- An electromagnetic clutch 14 serving as a power transmission device is interposed in the power transmission path 13 .
- the electromagnetic clutch 14 is mounted on the compressor.
- the electromagnetic clutch 14 includes a rotor 16 .
- the rotor 16 is rotatably supported by an outer circumferential surface of the housing 2 through a bearing 18 .
- the rotor 16 has an end face 16 a located on the side of the one end portion 10 of the rotary shaft 4 , and is also formed as a driving pulley 20 .
- the driving pulley 20 is connected to the power transmission path 13 , more specifically, to an output pulley (not shown) of the driving source 15 through an endless driving belt (not shown). Accordingly, when a driving force is transmitted from the driving source 15 to the driving pulley 20 , the driving pulley 20 , or the rotor 16 , is rotated in one direction.
- the electromagnetic clutch 14 has a clutch mechanism 24 .
- the clutch mechanism 24 will be described below in detail.
- the clutch mechanism 24 includes an electromagnetic solenoid 22 located in the inside of the rotor 16 .
- the electromagnetic solenoid 22 is fixed onto the outer circumferential surface of the housing 2 through a ring-shaped bracket 21 .
- the clutch mechanism 24 further includes a first rotation member, that is, a disc-shaped armature 26 .
- the armature 26 is disposed opposed to the one end face 16 a of the rotor 16 .
- the armature 26 has a circular opening 27 in the center thereof. As illustrated in FIG. 1 , when the electromagnetic clutch 14 is in a resting state, there is secured a given gap amount L between the armature 26 and the one end face 16 a of the rotor 16 .
- the armature 26 is coupled to an inner support 31 serving as a second rotation member through a spring unit 28 .
- the spring unit 28 is set in an outer surface of the armature 26 , that is, in an opposite face to the rotor 16 .
- the spring unit 28 has an outer ring 30 and a spring element 32 that is interfitted in the outer ring 30 .
- the spring element 32 is made of synthetic rubber and formed to have a ring-like shape. As is apparent from FIG. 1 , the spring element 32 integrally has a plurality of projections 32 a in an inner circumference thereof.
- the projections 32 a are arranged at regular intervals in a circumferential direction of the spring unit 28 and are in contact with the armature 26 .
- the outer ring 30 is made of metal and integrally has three lugs 33 in an outer circumference thereof.
- the lugs 33 are arranged at regular intervals in a circumferential direction of the outer ring 30 , and fixed on the armature 26 by using rivets 34 .
- the spring unit 28 is accordingly coupled to the armature 26 in an outer circumferential portion thereof.
- FIG. 1 shows only one of the lugs 33 and one of the rivets 34 .
- the inner support 31 is made of metal and has a disc-like shape.
- the inner support 31 has a rim 31 a in an outer circumference thereof.
- the rim 31 a bears the spring element 32 in consort with the outer ring 30 so that the spring element 32 is sandwiched between the rim 31 a and the outer ring 30 , and is fixed on the spring element 32 .
- the inner support 31 is coupled to the armature 26 serving as the first rotation member with the spring unit 28 intervening therebetween.
- the inner support 31 is fitted to a hub 48 in an inner circumferential portion thereof.
- the hub 48 is mounted on the one end portion 10 of the rotary shaft 4 .
- the inner support 31 has a circular opening 42 positioned in the center thereof and three bores 40 arranged outside the opening 42 .
- the bores 40 are distributed on the same circle and arranged at regular intervals in a circumferential direction of the inner support 31 .
- the inner support 31 further has three bores 41 .
- the bores 41 are arranged in the circumferential direction of the inner support 31 so that each of the bores 41 is located between two adjacent bores 40 .
- opening 42 and the bores 40 and 41 of the inner support 31 are disposed within an area with a smaller diameter than that of the opening 27 of the armature 26 .
- the hub 48 has a shape of a stepped hollow cylinder.
- Formed in the hub 48 is an axial bore 49 .
- the axial bore 49 extends along an axis of the hub 48 and passes through the hub 48 .
- the axial bore 49 has a female spline 50 f in the center thereof, and one end portion of the axial bore 49 , which is located on the side of the inner support 31 , is formed as a circular recessed area 51 .
- the recessed area 51 has a larger internal diameter than that of the axial bore 49 .
- a male spline 50 m is formed on the one end portion 10 of the rotary shaft 4 .
- the one end portion 10 has a male thread 10 a that is formed in an outer circumferential surface thereof so as to extend from the male spline 50 m to a tip end of the one end portion 10 .
- the male spline 50 m is engaged with the female spline 50 f of the axial bore 49 . This allows the hub 48 to rotate integrally with the rotary shaft 4 , relative to the circumferential direction of the rotary shaft 4 .
- the male thread 10 a of the rotary shaft 4 is located within the recessed area of the hub 48 .
- a nut 11 is screwed on the male thread 10 a , thereby interlocking the hub 48 to the rotary shaft 4 .
- the hub 48 has a flange 52 located in the one end side of the axial bore 49 .
- the flange 52 is protruding outward in a radial direction of the hub 48 .
- the flange 52 has an external diameter that is slightly smaller than the internal diameter of the opening 27 of the armature 26 .
- Formed in the flange 52 are three screw holes 56 , which are distributed on the same circle and arranged at regular intervals in a circumferential direction of the hub 48 .
- the distribution circle of the screw holes 56 has the same diameter as the distribution circle of the bores 40 of the inner support 31 . Therefore, as is apparent from FIG. 2 , the screw holes 56 can be positioned coaxially with the respective bores 40 .
- three circular recesses 53 are formed in the flange 52 .
- the circular recesses 53 correspond to the respective bores 41 of the inner support 31 .
- the hub 48 further includes an annular projection 58 in one end face thereof which is located on the flange 52 side.
- the annular projection 58 has an external diameter slightly smaller than an internal diameter of the opening 42 of the inner support 31 . Therefore, as is evident from FIG. 1 , the inner support 31 is fitted on the hub 48 in a state where the annular projection 58 is inserted in the opening 42 . At this moment, the bores 40 of the inner support 31 coincide with the respective screw holes 56 .
- the annular projection 58 has an internal diameter identical to an internal diameter of the recessed area 51 .
- a shim 62 is sandwiched between the inner support 31 and the flange 52 of the hub 48 .
- the shim 62 is used to secure the gap L.
- the inner support 31 and the flange 52 of the hub 48 have flat receiving faces 38 and 54 , respectively, with respect to the shim 62 .
- the shim 62 is formed into a disc and has substantially the same external diameter as the flange 52 of the hub 48 . Both sides of the shim 62 are formed as flat contact faces 64 a and 64 b to be in close contact with the receiving faces 38 and 54 , respectively.
- the shim 62 has an opening 66 located in the center thereof, three bores 68 arranged outside of the opening 66 , and three bores 65 each arranged between the respective two adjacent bores 68 .
- the opening 66 is allowed to coincide with the opening 42 of the inner support 31 , and the bores 68 and 65 with the respective bores 40 and 41 of the inner support 31 .
- the hub 48 is firstly spline-engaged with the one end portion 10 of the rotary shaft 4 , and the hub 48 is fixed onto the rotary shaft 4 with the nut 11 .
- the shim 62 is mounted on the annular projection 58 of the hub 48 , the armature 26 and the inner support 31 provided with the spring unit 28 are fixed to the hub 48 .
- the shim 62 is sandwiched between the inner support 31 and the flange 52 of the hub 48 , and the gap L is created due to thickness of the shim 62 .
- the electromagnetic solenoid 22 when the electromagnetic solenoid 22 is supplied with electric power, the electromagnetic solenoid 22 attracts the armature 26 while elastically deforming the spring element 32 of the spring unit 28 , thereby frictionally engaging the armature 26 and the rotor 16 with each other. At this point, the rotation of the rotor 16 is transmitted to the rotary shaft 4 through the armature 26 , the spring unit 28 , the inner support 31 , and the hub 48 . The rotary shaft 4 then rotates together with the rotor 16 and drives the compression unit 12 .
- the spring element 32 of the spring unit 28 detaches the armature 26 from the rotor 16 by using a restoring force thereof, thereby securing the gap L between the armature 26 and the rotor 16 .
- the rotation of the rotor 16 is not transmitted to the rotary shaft 4 , which stops the driving of the compression unit 12 .
- the shim 62 that secures the given gap L between the rotor 16 and the armature 26 when the electromagnetic clutch 14 is in the resting state, is sandwiched between the inner support 31 of the clutch mechanism 24 and the hub 48 . Consequently, the rotary shaft 4 does not need a stepped face formed by reducing the diameter of the rotary shaft 4 to sandwich a shim between the rotary shaft 4 and the hub 48 .
- the rotary shaft 4 can be reduced in diameter regardless of the shim 62 , and the sealing performance of the mechanical seal 6 is stably assured for a long term.
- the shim 62 includes the large contact faces 64 a and 64 b with respect to the inner support 31 and the hub 48 , surface pressure that is applied to the shim 62 is drastically reduced. This also decreases abrasion of the shim 62 which is caused by vibrations of the armature 26 . The shim 62 then stably retains the gap L for a long period and assures a stable operation of the electromagnetic clutch 14 .
- compressors according to second and third embodiments will be described below. Throughout the description about the compressors according to the second and third embodiments, members and portions identical to those of the compressor of the first embodiment will be referred by identical reference marks, and descriptions thereof will be omitted. Differences from the first embodiment will be explained below.
- the compressor according to the second embodiment has a torque limiter 14 A instead of the electromagnetic clutch 14 .
- the torque limiter 14 A includes a clutch mechanism 24 A that connects the rotor 16 and the rotary shaft 4 to each other.
- the clutch mechanism 24 A has a spring unit 28 A as a first rotation member.
- the lugs 33 of the spring unit 28 A instead of the rivets 34 of the first embodiment, are fixed to the rotor 16 with bolts 34 A.
- the spring unit 28 A includes an inner ring 78 made of metal.
- a spring element 32 is sandwiched between the inner ring 78 and the outer ring 30 .
- the spring element 32 is interfitted both in the outer ring 30 and the inner ring 78 .
- the inner support 31 A is disposed in the inside of the inner ring 78 .
- the inner support 31 A is not connected to either the inner ring 78 or the spring element 32 , thereby being in a state detached from both the inner ring 78 and the spring element 32 .
- a boss 35 is formed in the center of an outer surface of the inner support 31 A.
- the boss 35 has a male screw 37 in an outer circumferential surface thereof.
- a circular recessed area 39 is formed in an inner surface of the inner support 31 A.
- the recessed area 39 has an internal diameter and depth that are identical to an external diameter and thickness of a flange 52 A of the hub 48 A. Therefore, as is evident from FIG. 6 , the inner support 31 A is fitted to the hub 48 A in a state receiving the flange 52 A of the hub 48 A in the recessed area 39 , and is fastened to the hub 48 A with a plurality of connecting bolts 46 .
- An annular projection 58 A of the hub 48 A extends in an axial direction of the hub 48 A and is interfitted in an opening 42 of the boss 35 .
- Disposed between the boss 35 and the spring element 32 is a pressure plate 72 .
- the pressure plate 72 is fastened to the boss 35 with a washer 46 B and a nut 46 A intervening therebetween, and the nut 46 A is screwed on the male thread 37 of the boss 35 .
- the pressure plate 72 defines an annular accommodation chamber 73 in cooperation with the boss 35 , the spring element 32 , the inner ring 78 and the inner support 31 A.
- the accommodation chamber 73 is surrounded by the above-mentioned members 31 A, 32 , 35 and 78 .
- a plurality of balls 70 are contained in the accommodation chamber 73 .
- the balls 70 have outer surfaces that have been subjected to hardening treatment, and are arranged at regular intervals in a circumferential direction of the inner support 31 A.
- the pressure plate 72 has a tapered face 72 a in an inner surface on the side of the accommodation chamber 73 .
- the tapered face 72 a gradually reduces width of the accommodation chamber 73 along an axial direction of the boss 35 toward the boss 35 .
- the inner support 31 A has an annular projection 76 and an annular clearance groove 74 in the inner surface on the side of the accommodation chamber 73 .
- the clearance groove 74 is located more inside than the annular projection 76 , as viewed in a radial direction of the inner support 31 A.
- the balls 70 are held between the tapered face 72 a of the pressure plate 72 and the annular projection 76 of the inner support 31 A.
- the balls 70 are also in a state pressed against the inner ring 78 by an urging ring 80 such as a spiral spring.
- the urging ring 80 is contained in the accommodation chamber 73 .
- a bottom face of the recessed area 39 in the inner support 31 A is formed as the flat receiving face 38 .
- a shim 62 A is sandwiched between the receiving face 38 and a receiving face 54 of the hub 48 A. The shim 62 A adjusts the position of the inner support 31 A relative to the axial direction of the rotary shaft 4 , secures the given gap L between the spring element 32 and the rotor 16 , and prevents the spring element 32 from contacting the rotor 16 .
- the shim 62 A provides the compressor with similar advantages as with the shim 62 of the first embodiment.
- FIGS. 7 to 9 show the compressor according to the third embodiment.
- the compressor of the third embodiment has an electromagnetic clutch 14 B.
- the electromagnetic clutch 14 B includes, instead of the connecting bolts 46 of the first embodiment, a plurality of hollow pins 46 B for fastening an inner support 31 B to a hub 48 B. Therefore, as illustrated in FIG. 8 , the inner support 31 B has bores 44 instead of the bores 40 of the first embodiment, whereas the hub 48 B has through holes 60 instead of the screw holes 56 of the first embodiment.
- a shim 62 B has three bores 68 B instead of the bores 68 of the first embodiment.
- the hollow pins 46 B are inserted into the respective through holes 60 of the hub 48 B through the bores 44 of the inner support 31 B and the bores 68 B of the shim 62 B, thereby fitting the inner support 31 B to the hub 48 B.
- the shim 62 B of the third embodiment also exhibits similar advantages as with the shim 62 of the first embodiment.
- the connection of the inner support 31 B and the hub 48 B is achieved by insertion of the hollow pins 46 B. Therefore, the connection is easy, and also the radial positioning of the inner support 31 B in relation to the hub 48 B can be carried out with accuracy. Consequently, the compressor is greatly improved in productivity.
- the hollow pins 46 B are suitable for power transmission from the inner support 31 B to the hub 48 B. Load, especially a shearing force, applied to the hollow pins 46 B is reduced.
- FIG. 10 relates to connection of an inner support 31 C and a hub 48 C and shows a modification example thereof.
- the inner support 31 C integrally includes protruding portions 82
- the hub 48 C has recess portions 84 in which the protruding portions 82 are inserted, respectively. Therefore, the inner support 31 C and the hub 48 C are connected to each other by fitting the protruding portions 82 into the recess portions 84 . In this process, the protruding portions 82 penetrate bores of a shim 62 C.
- the protruding portions 82 and the recess portions 84 form a faucet joint.
- a faucet joint can include the protruding portions 82 formed in the hub 48 C and the recess portions 84 formed in the inner support 31 C.
- the invention is not limited to the compressors according to the first to fourth embodiments.
- the torque limiter may be a notch type including a break-away notch, instead of the ball type shown in FIG. 6 .
- a notch-type torque limiter is broken at a notch when overload is applied to the notch, and breaks power transmission from a rotor to a rotary shaft.
Abstract
A compressor of the present invention having an electromagnetic clutch (14) for transmitting a driving force from a driving source (15) to a rotary shaft (4), in which the clutch (14) includes a rotor (16) rotated by receiving the driving force of the driving source (15), the rotor (16) containing an electromagnetic solenoid (22), a hub (48) fixed to the rotary shaft (4), and a clutch mechanism (24) capable of connecting the rotor (16) and the hub (48) to each other; the clutch mechanism (24) has an armature (26) attracted to the rotor (16) when the solenoid (22) is in an operating state, an inner support (31) coupled to the hub (48), and a shim (62) sandwiched between the inner support (31) and the hub (48); and the shim (62) determines the size of a gap (L) to be secured between the rotor (16) and the armature (26) when the solenoid (22) is in a resting state.
Description
- The present invention relates to a compressor and a power transmission device which are suitable for a refrigeration device using CO2 gas as refrigerant.
- A compressor of this type has a housing, which contains a compression unit. The compression unit carries out a sequence of processes, starting with suction of refrigerant, followed by compression and discharge of the refrigerant.
- The compression unit is connected to a rotary shaft which drives the compression unit. The rotary shaft is disposed within the housing, and both end portions of the rotary shaft are rotatably supported by the housing through bearings. The rotary shaft has one end that is protruding from the housing. This one end is connected to a driving source through a power transmission path. Therefore, when the driving force of the driving source is transmitted through the power transmission path to the rotary shaft, the rotary shaft is rotated, and this rotation drives the compression unit.
- For example, a power transmission device such as an electromagnetic clutch is also interposed in the power transmission path. The power transmission device controls the transmission of the driving force from the driving source to the compression unit.
- Meanwhile, the housing is filled with the refrigerant, so that the pressure in the housing is increased while the compression unit is driven. In order to prevent the refrigerant from leaking out of the housing, the compressor further includes a shaft sealing unit, namely, mechanical seal, which is set in between the rotary shaft and the housing. The mechanical seal is placed near the bearing that is located on the side of the one end of the rotary shaft, and seals the rotary shaft with respect to the housing.
- The mechanical seal includes a fixed seal face that surrounds the rotary shaft and a movable seal face that rotates with the rotary shaft and slides against the fixed seal face. The mechanical seal receives high pressure in the housing on the fixed seal face. Such sealing effect of the mechanical seal is generally presented by the product of fluid pressure (P) applied to the fixed and movable seal faces and peripheral velocity (V) of the movable seal face, that is, a PV value.
- If CO2 gas is used as refrigerant as mentioned above, the CO2 gas decreases burdens on the global environment as it has smaller global warming potential than chlorofluorocarbon (CFC) that is commonly used as refrigerant. In such a case, however, the compressor is required to compress CO2 into a high-pressure range where the CO2 comes into a super critical state. For this reason, during operation of the compressor, the pressure in the housing becomes approximately seven to ten times higher than the case in which CFC is used as refrigerant.
- The above-mentioned pressure increase in the housing raises the PV value to exceed an allowable level of the mechanical seal. The seal faces of the mechanical seal are then liable to be worn early. As a result, the mechanical seal cannot stably confine the high-pressure CO2 refrigerant in the housing for a long period. This produces the possibility that the CO2 refrigerant will leak out of the housing while the compressor is used.
- To prevent the leakage of the CO2 refrigerant by using the mechanical seal, it is necessary to decrease the PV value of the mechanical seal to the allowable level. To this end, the peripheral velocity (V) of the movable seal face is reduced. In this case, to be more specific, the diameter of the rotary shaft may be reduced.
- Meanwhile, when the power transmission device is an electromagnetic clutch, this electromagnetic clutch includes a rotor located on the driving source side and an armature located on the rotary shaft side. The rotor and the armature must be spaced away from each other with a given gap between them when the electromagnetic clutch is in a resting state (refer to gap α disclosed in Patent Document 1 mentioned below).
- In order to secure this gap, a ring-shaped shim is utilized. The shim is placed between the rotary shaft and the hub of the electromagnetic clutch. More specifically, one end portion of the rotary shaft is formed as a small-diameter shaft portion, which provides the rotary shaft with an annular stepped face that is opposed to the hub. When placed between the hub and the stepped face, the shim creates the gap between the rotor and the armature.
- However, if the diameter of the rotary shaft is reduced to decrease the PV value of the mechanical seal, and moreover the one end portion of the rotary shaft is formed into the small-diameter shaft portion to provide the stepped face, the rotary shaft will be deficient in mechanical strength at the small-diameter shaft portion, and will be incapable of carrying out a stable transmission of the driving force, or torque transmission, from the driving source to the compression unit. This might result in a fracture of the rotary shaft.
- It is an object of the present invention to provide a compressor and a power transmission device which secures durability of a shaft sealing unit while avoiding the lack of strength of a rotary shaft even when CO2 is used as a working fluid.
- In order to accomplish the above object, the compressor comprises a housing; a rotary shaft rotatably supported in the housing, the rotary shaft having one end protruding from the housing; a compression unit contained in the housing, the compression unit for performing a sequence of processes, starting with suction of a working fluid, followed by compression and discharge of the working fluid, when driven by the rotary shaft; a shaft sealing unit disposed between the housing and the rotary shaft, for airtightly sealing the inside of the housing; and a power transmission device for transmitting a driving force from a driving source to the one end of the rotary shaft.
- The power transmission device includes a rotor rotatably supported by an outer surface of the housing through a bearing, for receiving the driving force from the driving source; a hub coupled to the one end of the rotary shaft, for rotating with the rotary shaft; a clutch mechanism for controlling transmission of rotational force from the rotor to the hub, the clutch mechanism including a first rotation member disposed adjacent to the rotor in relation to an axial direction of the rotary shaft, the first rotation member being capable of receiving the rotational force of the rotor and a second rotation member disposed adjacent to the hub in relation to the axial direction, the second rotation member being coupled to the hub and capable of receiving the rotational force of the first rotation member; and a shim sandwiched between the second rotation member and the hub, the shim determining a position of the first rotation member with respect to the rotor relative in the axial direction.
- In the above compressor, the shim is placed not between the hub and the rotary shaft but between the hub and the second rotation member. Therefore, the rotary shaft is not required to be reduced in diameter due to the placement of the shim. The diameter of the rotary shaft can be reduced only in consideration of use of CO2 gas as a working fluid, so that the diameter of the rotary shaft is not undesirably reduced. This makes it possible to secure durability of a shaft-sealing unit for a long term while avoiding the lack of mechanical strength in the rotary shaft, thereby significantly improving reliability of the compressor.
- To be concrete, the power transmission device is an electromagnetic clutch including an electromagnetic solenoid disposed within the rotor. In this case, the first rotation member of the clutch mechanism includes an armature for receiving the rotational force of the rotor when the electromagnetic solenoid is in an operating state and the armature is attracted to the rotor by the electromagnetic solenoid, and a spring element for urging the armature to secure a gap between the rotor and the armature in the axial direction, when the electromagnetic solenoid is in a resting state, the shim determining a size of the gap.
- The power transmission device may be a torque limiter for breaking transmission of the rotational force from the rotor to the rotary shaft when the rotary shaft comes into a locked state. In this case, the shim is used for position adjustment of the spring element and the rotor.
- No matter whether the power transmission device is the electromagnetic clutch or the torque limiter, the shim located between the hub and the second rotation member can have a larger pressure-receiving area than that of a shim located between the hub and the rotary shaft. Consequently, the shim is never buckled at the time of screw fastening for fixing the hub. Abrasion of the shim due to a tremor caused by variable load is also reduced.
- The clutch mechanism further includes a fastening element disposed in either one of the second rotation member and the hub, and a receiving element disposed in the other of the second rotation member and the hub, for receiving the fastening element to couple the second rotation member and the hub to each other. In this case, the shim has a bore into which the fastening element is inserted. More specifically, the fastening element is any one of a bolt, a pin, and a protruding portion integrally formed in one or the other of the second rotation member and the hub.
- The fastening element and the receiving element easily and firmly couple the second rotation member and the hub to each other, and are greatly useful for improving the productivity of the compressor.
- The invention also provides the compressor using CO2 gas as a working fluid and the power transmission device included in the compressor.
-
FIG. 1 is a sectional view showing a part of a compressor according to a first embodiment; -
FIG. 2 is a sectional exploded view showing a part of a power transmission device ofFIG. 1 ; -
FIG. 3 is a front view of the power transmission device ofFIG. 1 ; -
FIG. 4 is a front view of a hub ofFIG. 2 ; -
FIG. 5 is a front view of a shim ofFIG. 2 ; -
FIG. 6 is a sectional view showing a part of a compressor according to a second embodiment; -
FIG. 7 is a sectional view showing a part of a compressor according to a third embodiment; -
FIG. 8 is a front view of a power transmission device ofFIG. 7 ; -
FIG. 9 is a front view of a shim ofFIG. 7 ; and -
FIG. 10 is a sectional view showing a modification example of a coupling structure for connecting an inner support and the hub ofFIG. 2 to each other. -
FIG. 1 shows a part of a compressor according to a first embodiment. The compressor is contained in a refrigeration device using CO2 as refrigerant. More specifically, the refrigeration plat is included in a vehicle air conditioning system. - The compressor has a
housing 2.FIG. 1 only shows a part of thehousing 2. In thehousing 2, there is disposed arotary shaft 4, which is rotatably supported through bearings (not shown) with respect to thehousing 2. - A
mechanical seal 6 serving as a shaft sealing unit is also located in thehousing 2. Themechanical seal 6 keeps an airtight condition between thehousing 2 and therotary shaft 4. More specifically, themechanical seal 6 includes asheet 7 a fixed to thehousing 2 and aseal ring 7 b fitted to therotary shaft 4 and pressed against thesheet 7 a. Thesheet 7 a and theseal ring 7 b have annular seal faces 8 a and 8 b that are in close contact. - Instead of the
mechanical seal 6, lip seals (not shown) may be utilized as the shaft sealing unit. The lip seal is placed between therotary shaft 4 and thehousing 2 and has a cylindrical seal face. - The
rotary shaft 4 has oneend portion 10 protruding from thehousing 2 and the other end portion (not shown) that is positioned within thehousing 2. The other end portion of therotary shaft 4 is connected to acompression unit 12. Thecompression unit 12 is accommodated in thehousing 2 and is driven by therotary shaft 4. Specifically, thecompression unit 12 is, for example, either one of a swash-plate compression unit including a piston that makes a reciprocating motion according to therotary shaft 4 and a scroll compression unit including a movable scroll that makes an orbiting motion according to therotary shaft 4. - When driven, the
compression unit 12 repeatedly performs a sequence of processes, starting with suction of CO2 refrigerant, followed by compression and discharge of the CO2 refrigerant, thereby circulating the CO2 refrigerant through a refrigerant circuit of the refrigeration device. - As illustrated in
FIG. 1 , the oneend portion 10 of therotary shaft 4 is connected to a drivingsource 15 through apower transmission path 13. The drivingsource 15 is either an engine or motor of a vehicle. An electromagnetic clutch 14 serving as a power transmission device is interposed in thepower transmission path 13. Theelectromagnetic clutch 14 is mounted on the compressor. - More specifically, the
electromagnetic clutch 14 includes arotor 16. Therotor 16 is rotatably supported by an outer circumferential surface of thehousing 2 through abearing 18. Therotor 16 has anend face 16 a located on the side of the oneend portion 10 of therotary shaft 4, and is also formed as a drivingpulley 20. The drivingpulley 20 is connected to thepower transmission path 13, more specifically, to an output pulley (not shown) of the drivingsource 15 through an endless driving belt (not shown). Accordingly, when a driving force is transmitted from the drivingsource 15 to the drivingpulley 20, the drivingpulley 20, or therotor 16, is rotated in one direction. - The
electromagnetic clutch 14 has aclutch mechanism 24. Theclutch mechanism 24 will be described below in detail. - The
clutch mechanism 24 includes anelectromagnetic solenoid 22 located in the inside of therotor 16. Theelectromagnetic solenoid 22 is fixed onto the outer circumferential surface of thehousing 2 through a ring-shapedbracket 21. - The
clutch mechanism 24 further includes a first rotation member, that is, a disc-shapedarmature 26. Thearmature 26 is disposed opposed to the oneend face 16 a of therotor 16. Thearmature 26 has acircular opening 27 in the center thereof. As illustrated inFIG. 1 , when theelectromagnetic clutch 14 is in a resting state, there is secured a given gap amount L between thearmature 26 and the oneend face 16 a of therotor 16. - The
armature 26 is coupled to aninner support 31 serving as a second rotation member through aspring unit 28. Thespring unit 28 is set in an outer surface of thearmature 26, that is, in an opposite face to therotor 16. Thespring unit 28 has anouter ring 30 and aspring element 32 that is interfitted in theouter ring 30. Thespring element 32 is made of synthetic rubber and formed to have a ring-like shape. As is apparent fromFIG. 1 , thespring element 32 integrally has a plurality ofprojections 32 a in an inner circumference thereof. Theprojections 32 a are arranged at regular intervals in a circumferential direction of thespring unit 28 and are in contact with thearmature 26. - The
outer ring 30 is made of metal and integrally has threelugs 33 in an outer circumference thereof. Thelugs 33 are arranged at regular intervals in a circumferential direction of theouter ring 30, and fixed on thearmature 26 by usingrivets 34. Thespring unit 28 is accordingly coupled to thearmature 26 in an outer circumferential portion thereof.FIG. 1 shows only one of thelugs 33 and one of therivets 34. - The
inner support 31 is made of metal and has a disc-like shape. Theinner support 31 has arim 31 a in an outer circumference thereof. Therim 31 a bears thespring element 32 in consort with theouter ring 30 so that thespring element 32 is sandwiched between therim 31 a and theouter ring 30, and is fixed on thespring element 32. In short, theinner support 31 is coupled to thearmature 26 serving as the first rotation member with thespring unit 28 intervening therebetween. - The
inner support 31 is fitted to ahub 48 in an inner circumferential portion thereof. Thehub 48 is mounted on the oneend portion 10 of therotary shaft 4. More concretely, as illustrated inFIGS. 2 and 3 , theinner support 31 has acircular opening 42 positioned in the center thereof and threebores 40 arranged outside theopening 42. Thebores 40 are distributed on the same circle and arranged at regular intervals in a circumferential direction of theinner support 31. Theinner support 31 further has three bores 41. Thebores 41 are arranged in the circumferential direction of theinner support 31 so that each of thebores 41 is located between twoadjacent bores 40. - It should be noted that the
opening 42 and thebores inner support 31 are disposed within an area with a smaller diameter than that of theopening 27 of thearmature 26. - As is evident from
FIG. 2 , thehub 48 has a shape of a stepped hollow cylinder. Formed in thehub 48 is anaxial bore 49. Theaxial bore 49 extends along an axis of thehub 48 and passes through thehub 48. As viewed in the axial direction of thehub 48, theaxial bore 49 has afemale spline 50 f in the center thereof, and one end portion of theaxial bore 49, which is located on the side of theinner support 31, is formed as a circular recessedarea 51. The recessedarea 51 has a larger internal diameter than that of theaxial bore 49. - A
male spline 50 m is formed on the oneend portion 10 of therotary shaft 4. The oneend portion 10 has amale thread 10 a that is formed in an outer circumferential surface thereof so as to extend from themale spline 50 m to a tip end of the oneend portion 10. When the oneend portion 10 of therotary shaft 4 is inserted into theaxial bore 49 of thehub 48 from the other end side thereof, themale spline 50 m is engaged with thefemale spline 50 f of theaxial bore 49. This allows thehub 48 to rotate integrally with therotary shaft 4, relative to the circumferential direction of therotary shaft 4. - When the above-mentioned spline engagement is completed, the
male thread 10 a of therotary shaft 4 is located within the recessed area of thehub 48. As illustrated inFIG. 1 , anut 11 is screwed on themale thread 10 a, thereby interlocking thehub 48 to therotary shaft 4. - The
hub 48 has aflange 52 located in the one end side of theaxial bore 49. Theflange 52 is protruding outward in a radial direction of thehub 48. Theflange 52 has an external diameter that is slightly smaller than the internal diameter of theopening 27 of thearmature 26. Formed in theflange 52 are threescrew holes 56, which are distributed on the same circle and arranged at regular intervals in a circumferential direction of thehub 48. The distribution circle of the screw holes 56 has the same diameter as the distribution circle of thebores 40 of theinner support 31. Therefore, as is apparent fromFIG. 2 , the screw holes 56 can be positioned coaxially with the respective bores 40. - Referring to
FIG. 4 for more precision, threecircular recesses 53 are formed in theflange 52. The circular recesses 53 correspond to therespective bores 41 of theinner support 31. - As illustrated in
FIG. 2 , thehub 48 further includes anannular projection 58 in one end face thereof which is located on theflange 52 side. Theannular projection 58 has an external diameter slightly smaller than an internal diameter of theopening 42 of theinner support 31. Therefore, as is evident fromFIG. 1 , theinner support 31 is fitted on thehub 48 in a state where theannular projection 58 is inserted in theopening 42. At this moment, thebores 40 of theinner support 31 coincide with the respective screw holes 56. Theannular projection 58 has an internal diameter identical to an internal diameter of the recessedarea 51. - At the time of the fixing of the
inner support 31 to thehub 48, as is apparent fromFIG. 2 , ashim 62 is sandwiched between theinner support 31 and theflange 52 of thehub 48. Theshim 62 is used to secure the gap L. - To be more concrete, the
inner support 31 and theflange 52 of thehub 48 have flat receiving faces 38 and 54, respectively, with respect to theshim 62. Theshim 62 is formed into a disc and has substantially the same external diameter as theflange 52 of thehub 48. Both sides of theshim 62 are formed as flat contact faces 64 a and 64 b to be in close contact with the receiving faces 38 and 54, respectively. - As is obvious from
FIG. 5 , theshim 62 has anopening 66 located in the center thereof, threebores 68 arranged outside of theopening 66, and threebores 65 each arranged between the respective twoadjacent bores 68. Theopening 66 is allowed to coincide with theopening 42 of theinner support 31, and thebores respective bores inner support 31. - To mount the
clutch mechanism 24 on therotary shaft 4, thehub 48 is firstly spline-engaged with the oneend portion 10 of therotary shaft 4, and thehub 48 is fixed onto therotary shaft 4 with thenut 11. After theshim 62 is mounted on theannular projection 58 of thehub 48, thearmature 26 and theinner support 31 provided with thespring unit 28 are fixed to thehub 48. As a result, theshim 62 is sandwiched between theinner support 31 and theflange 52 of thehub 48, and the gap L is created due to thickness of theshim 62. Thereafter, as is apparent fromFIG. 1 , three connectingbolts 46 are screwed into the respective screw holes 56 of theflange 52 through thebores inner support 31 and theshim 62. As a result, theinner support 31 is interlocked with therotary shaft 4 with thehub 48 intervening therebetween. - In the electromagnetic clutch 14, when the
electromagnetic solenoid 22 is supplied with electric power, theelectromagnetic solenoid 22 attracts thearmature 26 while elastically deforming thespring element 32 of thespring unit 28, thereby frictionally engaging thearmature 26 and therotor 16 with each other. At this point, the rotation of therotor 16 is transmitted to therotary shaft 4 through thearmature 26, thespring unit 28, theinner support 31, and thehub 48. Therotary shaft 4 then rotates together with therotor 16 and drives thecompression unit 12. - When the electric power supply to the
electromagnetic solenoid 22 is stopped, thespring element 32 of thespring unit 28 detaches thearmature 26 from therotor 16 by using a restoring force thereof, thereby securing the gap L between thearmature 26 and therotor 16. In such a resting state of the electromagnetic clutch 14, accordingly, the rotation of therotor 16 is not transmitted to therotary shaft 4, which stops the driving of thecompression unit 12. - In the compressor according to the first embodiment, the
shim 62, that secures the given gap L between therotor 16 and thearmature 26 when theelectromagnetic clutch 14 is in the resting state, is sandwiched between theinner support 31 of theclutch mechanism 24 and thehub 48. Consequently, therotary shaft 4 does not need a stepped face formed by reducing the diameter of therotary shaft 4 to sandwich a shim between therotary shaft 4 and thehub 48. - For that reason, when the compressor of the first embodiment uses a CO2 refrigerant, the
rotary shaft 4 can be reduced in diameter regardless of theshim 62, and the sealing performance of themechanical seal 6 is stably assured for a long term. - Since the
shim 62 includes the large contact faces 64 a and 64 b with respect to theinner support 31 and thehub 48, surface pressure that is applied to theshim 62 is drastically reduced. This also decreases abrasion of theshim 62 which is caused by vibrations of thearmature 26. Theshim 62 then stably retains the gap L for a long period and assures a stable operation of theelectromagnetic clutch 14. - Since the
inner support 31 and thehub 48 are connected to each other with the connectingbolts 46, it is easy to achieve a firm engagement between theinner support 31 and thehub 48. - Compressors according to second and third embodiments will be described below. Throughout the description about the compressors according to the second and third embodiments, members and portions identical to those of the compressor of the first embodiment will be referred by identical reference marks, and descriptions thereof will be omitted. Differences from the first embodiment will be explained below.
- Referring to
FIG. 6 , the compressor according to the second embodiment has atorque limiter 14A instead of theelectromagnetic clutch 14. Thetorque limiter 14A includes aclutch mechanism 24A that connects therotor 16 and therotary shaft 4 to each other. - The
clutch mechanism 24A has aspring unit 28A as a first rotation member. Thelugs 33 of thespring unit 28A, instead of therivets 34 of the first embodiment, are fixed to therotor 16 withbolts 34A. - The
spring unit 28A includes aninner ring 78 made of metal. Aspring element 32 is sandwiched between theinner ring 78 and theouter ring 30. Thespring element 32 is interfitted both in theouter ring 30 and theinner ring 78. - The
inner support 31A is disposed in the inside of theinner ring 78. Theinner support 31A is not connected to either theinner ring 78 or thespring element 32, thereby being in a state detached from both theinner ring 78 and thespring element 32. - A
boss 35 is formed in the center of an outer surface of theinner support 31A. Theboss 35 has amale screw 37 in an outer circumferential surface thereof. A circular recessedarea 39 is formed in an inner surface of theinner support 31A. The recessedarea 39 has an internal diameter and depth that are identical to an external diameter and thickness of aflange 52A of thehub 48A. Therefore, as is evident fromFIG. 6 , theinner support 31A is fitted to thehub 48A in a state receiving theflange 52A of thehub 48A in the recessedarea 39, and is fastened to thehub 48A with a plurality of connectingbolts 46. - An
annular projection 58A of thehub 48A extends in an axial direction of thehub 48A and is interfitted in anopening 42 of theboss 35. Disposed between theboss 35 and thespring element 32 is apressure plate 72. Thepressure plate 72 is fastened to theboss 35 with awasher 46B and anut 46A intervening therebetween, and thenut 46A is screwed on themale thread 37 of theboss 35. - The
pressure plate 72 defines anannular accommodation chamber 73 in cooperation with theboss 35, thespring element 32, theinner ring 78 and theinner support 31A. In other words, theaccommodation chamber 73 is surrounded by the above-mentionedmembers balls 70 are contained in theaccommodation chamber 73. Theballs 70 have outer surfaces that have been subjected to hardening treatment, and are arranged at regular intervals in a circumferential direction of theinner support 31A. - The
pressure plate 72 has a taperedface 72 a in an inner surface on the side of theaccommodation chamber 73. The taperedface 72 a gradually reduces width of theaccommodation chamber 73 along an axial direction of theboss 35 toward theboss 35. Theinner support 31A has anannular projection 76 and anannular clearance groove 74 in the inner surface on the side of theaccommodation chamber 73. Theclearance groove 74 is located more inside than theannular projection 76, as viewed in a radial direction of theinner support 31A. - In a state shown in
FIG. 6 , theballs 70 are held between thetapered face 72 a of thepressure plate 72 and theannular projection 76 of theinner support 31A. Theballs 70 are also in a state pressed against theinner ring 78 by an urgingring 80 such as a spiral spring. The urgingring 80 is contained in theaccommodation chamber 73. - According to the second embodiment, a bottom face of the recessed
area 39 in theinner support 31A is formed as the flat receivingface 38. Ashim 62A is sandwiched between the receivingface 38 and a receivingface 54 of thehub 48A. Theshim 62A adjusts the position of theinner support 31A relative to the axial direction of therotary shaft 4, secures the given gap L between thespring element 32 and therotor 16, and prevents thespring element 32 from contacting therotor 16. - In the compressor according to the second embodiment, when the
rotor 16 is supplied with the driving force and is rotated, the rotation of therotor 16 is transmitted to thehub 48A through thespring element 32, theinner ring 78, theballs 70, theannular projection 76 and theinner support 31A, and is then transmitted from thehub 48A to therotary shaft 4. - During the rotation of the
rotary shaft 4, when load applied to therotary shaft 4 is increased, and locking tendency or locking occurs on therotary shaft 4, there causes a great differential between a rotational velocity of therotor 16 and that of therotary shaft 4. Such a velocity differential applies great torque to therotor 16, so that theballs 70 fall into theclearance groove 74 of theinner support 31A by overcoming an urging force of the urgingmember 80 and friction engagement with respect to the taperedface 72 a of thepressure plate 72 and theannular projection 76 of theinner support 31A. As a result, theballs 70 fail to transmit the rotation of therotor 16 to theinner support 31A, which allows thetorque limiter 14B to exhibit its original function. - In the second embodiment, the
shim 62A provides the compressor with similar advantages as with theshim 62 of the first embodiment. -
FIGS. 7 to 9 show the compressor according to the third embodiment. - As is obvious from
FIG. 7 , the compressor of the third embodiment has an electromagnetic clutch 14B. The electromagnetic clutch 14B includes, instead of the connectingbolts 46 of the first embodiment, a plurality ofhollow pins 46B for fastening aninner support 31B to ahub 48B. Therefore, as illustrated inFIG. 8 , theinner support 31B hasbores 44 instead of thebores 40 of the first embodiment, whereas thehub 48B has throughholes 60 instead of the screw holes 56 of the first embodiment. Ashim 62B has threebores 68B instead of thebores 68 of the first embodiment. - The hollow pins 46B are inserted into the respective through
holes 60 of thehub 48B through thebores 44 of theinner support 31B and thebores 68B of theshim 62B, thereby fitting theinner support 31B to thehub 48B. - The
shim 62B of the third embodiment also exhibits similar advantages as with theshim 62 of the first embodiment. In the case of the compressor according to the third embodiment, the connection of theinner support 31B and thehub 48B is achieved by insertion of thehollow pins 46B. Therefore, the connection is easy, and also the radial positioning of theinner support 31B in relation to thehub 48B can be carried out with accuracy. Consequently, the compressor is greatly improved in productivity. - The hollow pins 46B are suitable for power transmission from the
inner support 31B to thehub 48B. Load, especially a shearing force, applied to thehollow pins 46B is reduced. -
FIG. 10 relates to connection of aninner support 31C and ahub 48C and shows a modification example thereof. - According to the modification example shown in
FIG. 10 , theinner support 31C integrally includes protrudingportions 82, and thehub 48C hasrecess portions 84 in which the protrudingportions 82 are inserted, respectively. Therefore, theinner support 31C and thehub 48C are connected to each other by fitting the protrudingportions 82 into therecess portions 84. In this process, the protrudingportions 82 penetrate bores of ashim 62C. - The protruding
portions 82 and therecess portions 84 form a faucet joint. Such a faucet joint can include the protrudingportions 82 formed in thehub 48C and therecess portions 84 formed in theinner support 31C. - The invention is not limited to the compressors according to the first to fourth embodiments.
- For instance, the torque limiter may be a notch type including a break-away notch, instead of the ball type shown in
FIG. 6 . A notch-type torque limiter is broken at a notch when overload is applied to the notch, and breaks power transmission from a rotor to a rotary shaft.
Claims (11)
1. A compressor comprising:
a housing;
a rotary shaft rotatably supported in said housing, said rotary shaft having one end protruding from said housing;
a compression unit contained in said housing, said compression unit for performing a sequence of processes, starting with suction of a working fluid, followed by compression and discharge of the working fluid, when driven by said rotary shaft;
a shaft sealing unit disposed between said housing and said rotary shaft, for airtightly sealing the inside of said housing; and
a power transmission device for transmitting a driving force from a driving source to the one end of said rotary shaft, wherein
said power transmission device includes:
a rotor rotatably supported by an outer surface of said housing through a bearing, for receiving the driving force from the driving source;
a hub coupled to the one end of said rotary shaft, for rotating with said rotary shaft;
a clutch mechanism for controlling transmission of rotational force from the rotor to the hub, the clutch mechanism including a first rotation member disposed adjacent to the rotor in relation to an axial direction of said rotary shaft, the first rotation member being capable of receiving the rotational force of the rotor, and a second rotation member disposed adjacent to the hub in relation to the axial direction, the second rotation member being coupled to the hub and capable of receiving the rotational force of the first rotation member; and
a shim sandwiched between the second rotation member and the hub, the shim determining a position of the first rotation member with respect to the rotor in the axial direction.
2. The compressor according to claim 1 , wherein:
said power transmission device is an electromagnetic clutch including an electromagnetic solenoid disposed within the rotor, wherein:
the first rotation member of the clutch mechanism includes:
an armature for receiving the rotational force of the rotor when the electromagnetic solenoid is in an operating state and the armature is attracted to the rotor by the electromagnetic solenoid, and
a spring element for urging the armature to secure a gap between the rotor and the armature in the axial direction when the electromagnetic solenoid is in a resting state, and wherein:
the shim determines a size of the gap.
3. The compressor according to claim 1 , wherein:
said power transmission device is a torque limiter for breaking transmission of the rotational force from the rotor to said rotary shaft when said rotary shaft comes into a locked state, wherein:
the first rotation member of the clutch mechanism includes a spring element connected to the rotor, and wherein:
the shim secures a gap between the rotor and the spring element in the axial direction.
4. The compressor according to claim 1 , wherein:
the clutch mechanism further includes a fastening element disposed in either one of the second rotation member and the hub, and a receiving element disposed in the other of the second rotation member and the hub, for receiving the fastening element to couple the second rotation member and the hub to each other, and wherein:
the shim has a bore into which the fastening element is inserted.
5. The compressor according to claim 4 , wherein:
the fastening element is any one of a bolt, a pin, and a protruding portion integrally formed in one or the other of the second rotation member and the hub.
6. The compressor according to claim 1 , wherein:
the working fluid includes CO2 gas.
7. A power transmission device for transmitting a driving force from a driving source to a rotary shaft, comprising:
a rotor rotatably disposed so as to be coaxial with the rotary shaft, for receiving the driving force from the driving source;
a hub coupled to the rotary shaft, for rotating with the rotary shaft;
a clutch mechanism for controlling transmission of rotational force from said rotor to said hub, said clutch mechanism including a first rotation member disposed adjacent to said rotor in relation to an axial direction of the rotary shaft, the first rotation member being capable of receiving the rotational force of said rotor, and a second rotation member disposed adjacent to said hub in relation to the axial direction, the second rotation member being coupled to said hub and capable of receiving rotational force of the first rotation member; and
a shim sandwiched between the second rotation member and said hub, said shim determining a position of the first rotation member with respect to said rotor in the axial direction, wherein:
the power transmission means is an electromagnetic clutch in which the rotor facing portion includes a clutch plate, the transmission body has an armature body, and the clutch plate is attracted to the rotor by power supply, and wherein:
the shim adjusts an axial position of the clutch plate.
8. The power transmission device according to claim 7 , wherein:
the power transmission device is an electromagnetic clutch including an electromagnetic solenoid disposed within said rotor, wherein:
the first rotation member of said clutch mechanism includes:
an armature for receiving the rotational force of said rotor when the electromagnetic solenoid is in an operating state and the armature is attracted to said rotor; and
a spring element for urging the armature to secure a gap between said rotor and the armature in the axial direction when the electromagnetic solenoid is in a resting state, and wherein:
the shim determines a size of the gap.
9. The power transmission device according to claim 7 , wherein:
the power transmission device is a torque limiter for breaking transmission of the rotational force from said rotor to the rotary shaft when the rotary shaft comes into a locked state, wherein:
the first rotation member of said clutch mechanism includes a spring element connected to the rotor, and wherein:
the shim secures a gap between said rotor and the spring element in the axial direction.
10. The power transmission device according to claim 7 , wherein:
said clutch mechanism further includes a fastening element disposed in either one of the second rotation member and said hub, and a receiving element disposed in the other of the second rotation member and said hub, and receives the fastening element to couple the second rotation member and said hub to each other, and wherein:
the shim has a bore into which the fastening element is inserted.
11. The power transmission device according to claim 10 , wherein:
the fastening element is any one of a bolt, a pin, and a protruding portion integrally formed in one or the other of the second rotation member and said hub.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2005295022A JP4713293B2 (en) | 2005-10-07 | 2005-10-07 | Compressor |
JP2005-295022 | 2005-10-07 | ||
PCT/JP2006/319989 WO2007043444A1 (en) | 2005-10-07 | 2006-10-05 | Compressor and power transmission device |
Publications (1)
Publication Number | Publication Date |
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US20090047162A1 true US20090047162A1 (en) | 2009-02-19 |
Family
ID=37942687
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/886,896 Abandoned US20090047162A1 (en) | 2005-10-07 | 2006-10-05 | Compressor and Power Transmission Device |
Country Status (5)
Country | Link |
---|---|
US (1) | US20090047162A1 (en) |
EP (1) | EP1933032B1 (en) |
JP (1) | JP4713293B2 (en) |
CN (1) | CN101155991B (en) |
WO (1) | WO2007043444A1 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100033170A1 (en) * | 2008-08-06 | 2010-02-11 | Haas Automation, Inc. | Rotary position encoder |
US20140179476A1 (en) * | 2012-12-24 | 2014-06-26 | Borgwarner Inc. | Metal Pulley With NonMagnetic Insert |
WO2014182350A1 (en) * | 2013-05-08 | 2014-11-13 | Eaton Corporation | Supercharger torsional compliance and damping features |
US20160076599A1 (en) * | 2014-09-17 | 2016-03-17 | Electro-Motive Diesel, Inc. | Assembly for preventing abuse of a pump mounted to a driver equipment |
US9447826B2 (en) | 2012-12-24 | 2016-09-20 | Borgwarner Inc. | Friction clutch for driven accessory |
US9458897B2 (en) | 2012-12-24 | 2016-10-04 | Borgwarner Inc. | Accessory drive with friction clutch |
US9482286B2 (en) | 2011-04-13 | 2016-11-01 | Borgwarner Inc. | Fail-safe dry friction clutch for a vehicle accessory |
US9863486B2 (en) | 2012-12-24 | 2018-01-09 | Borgwarner Inc. | Driven accessory |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009034808A1 (en) * | 2008-08-07 | 2010-02-11 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Double coupling |
DE202013002597U1 (en) * | 2013-03-18 | 2013-03-26 | Erwin A. Lang Gmbh & Co. Kg | Electromagnetic coupling device |
JP6248773B2 (en) * | 2014-04-17 | 2017-12-20 | 株式会社デンソー | Power transmission device |
JP6597746B2 (en) * | 2016-11-10 | 2019-10-30 | 株式会社デンソー | Power transmission device |
US10724592B2 (en) | 2017-04-20 | 2020-07-28 | Consolidated Metco, Inc. | High friction insulator |
KR102590950B1 (en) * | 2017-06-28 | 2023-10-19 | 한온시스템 주식회사 | Clutch and compressor having the same |
JP6747399B2 (en) * | 2017-07-28 | 2020-08-26 | 株式会社デンソー | Power transmission device |
CN109253174B (en) * | 2018-12-06 | 2023-06-30 | 上汽红岩车桥(重庆)有限公司 | Transmission structure of heavy-duty car |
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US5080213A (en) * | 1988-10-24 | 1992-01-14 | Sanden Corporation | Electromagnetic clutch with an adjusting means for adjusting a substantial length of a leaf spring which is for supporting an armature plate |
US5269661A (en) * | 1991-05-15 | 1993-12-14 | Sanden Corporation | Scroll type fluid displacement apparatus having a capacity control mechanism |
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US6533555B2 (en) * | 2000-06-13 | 2003-03-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor |
US6932729B2 (en) * | 2001-12-04 | 2005-08-23 | Sanden Corporation | Compressor having a power transmission mechanism which prevents balls from moving in an axial direction |
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JPH0266324A (en) * | 1988-08-31 | 1990-03-06 | Hitachi Ltd | Electromagnetic clutch |
JPH0874885A (en) * | 1994-09-07 | 1996-03-19 | Sanden Corp | Solenoid clutch |
JPH08135752A (en) * | 1994-09-14 | 1996-05-31 | Nippondenso Co Ltd | Power transmission device |
US5683299A (en) * | 1994-09-14 | 1997-11-04 | Nippondenso Co., Ltd. | Device for transmitting rotational power |
JP3480094B2 (en) * | 1995-02-06 | 2003-12-15 | 株式会社豊田自動織機 | Power cutoff mechanism in clutchless compressor |
JPH10115333A (en) * | 1996-10-11 | 1998-05-06 | Zexel Corp | Electromagnetic clutch |
JP2001173682A (en) * | 1999-12-15 | 2001-06-26 | Mitsubishi Heavy Ind Ltd | Electromagnetic clutch structure for compressor |
JP4888801B2 (en) * | 2001-05-22 | 2012-02-29 | 株式会社ヴァレオジャパン | Electromagnetic clutch |
-
2005
- 2005-10-07 JP JP2005295022A patent/JP4713293B2/en not_active Expired - Fee Related
-
2006
- 2006-10-05 WO PCT/JP2006/319989 patent/WO2007043444A1/en active Application Filing
- 2006-10-05 EP EP06821824.7A patent/EP1933032B1/en not_active Expired - Fee Related
- 2006-10-05 US US11/886,896 patent/US20090047162A1/en not_active Abandoned
- 2006-10-05 CN CN2006800093809A patent/CN101155991B/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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US3024963A (en) * | 1955-03-23 | 1962-03-13 | Gen Motors Corp | Refrigerating apparatus |
US5080213A (en) * | 1988-10-24 | 1992-01-14 | Sanden Corporation | Electromagnetic clutch with an adjusting means for adjusting a substantial length of a leaf spring which is for supporting an armature plate |
US5269661A (en) * | 1991-05-15 | 1993-12-14 | Sanden Corporation | Scroll type fluid displacement apparatus having a capacity control mechanism |
US5667050A (en) * | 1995-01-30 | 1997-09-16 | Ogura Clutch Co., Ltd. | Electromagnetic coupling apparatus |
US6533555B2 (en) * | 2000-06-13 | 2003-03-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor |
US6932729B2 (en) * | 2001-12-04 | 2005-08-23 | Sanden Corporation | Compressor having a power transmission mechanism which prevents balls from moving in an axial direction |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100033170A1 (en) * | 2008-08-06 | 2010-02-11 | Haas Automation, Inc. | Rotary position encoder |
US9518815B2 (en) * | 2008-08-06 | 2016-12-13 | Haas Automation, Inc. | Rotary position encoder for rotatable shafts |
US9482286B2 (en) | 2011-04-13 | 2016-11-01 | Borgwarner Inc. | Fail-safe dry friction clutch for a vehicle accessory |
US20140179476A1 (en) * | 2012-12-24 | 2014-06-26 | Borgwarner Inc. | Metal Pulley With NonMagnetic Insert |
US9447826B2 (en) | 2012-12-24 | 2016-09-20 | Borgwarner Inc. | Friction clutch for driven accessory |
US9453571B2 (en) * | 2012-12-24 | 2016-09-27 | Borgwarner Inc. | Metal pulley with non-magnetically susceptible insert |
US9458897B2 (en) | 2012-12-24 | 2016-10-04 | Borgwarner Inc. | Accessory drive with friction clutch |
US9765827B2 (en) | 2012-12-24 | 2017-09-19 | Borgwarner Inc. | Dry friction clutch for a vehicle accessory |
US9863486B2 (en) | 2012-12-24 | 2018-01-09 | Borgwarner Inc. | Driven accessory |
WO2014182350A1 (en) * | 2013-05-08 | 2014-11-13 | Eaton Corporation | Supercharger torsional compliance and damping features |
US20160076599A1 (en) * | 2014-09-17 | 2016-03-17 | Electro-Motive Diesel, Inc. | Assembly for preventing abuse of a pump mounted to a driver equipment |
US9790997B2 (en) * | 2014-09-17 | 2017-10-17 | Electro-Motive Diesel, Inc. | Assembly for preventing abuse of a pump mounted to a driver equipment |
Also Published As
Publication number | Publication date |
---|---|
JP2007100675A (en) | 2007-04-19 |
EP1933032B1 (en) | 2013-08-21 |
CN101155991A (en) | 2008-04-02 |
EP1933032A4 (en) | 2010-11-10 |
JP4713293B2 (en) | 2011-06-29 |
WO2007043444A1 (en) | 2007-04-19 |
CN101155991B (en) | 2010-06-09 |
EP1933032A1 (en) | 2008-06-18 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SANDEN CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:UCHIKADO, IWAO;IIZUKA, JIRO;REEL/FRAME:019923/0768 Effective date: 20070827 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |