JP2015158156A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the noise of a scroll compressor without size increase.SOLUTION: A swing link mechanism is constituted by a balancer integral bush 35 including a bush 35a that is a cylindrical member interposed between an eccentric portion 25b of a shaft 25 and an attachment hole 21c of a movable scroll 21 and a balancer 35b fixed to an outer circumference of the bush 35a and serving as an abutment member abutting a columnar portion 25a of the shaft 25 when the bush 35a rotates around the eccentric portion 25b. Furthermore, an annular groove is formed in a region on which the balancer 35b abuts, on an outer surface of the columnar portion 25a to arrange a buffer member formed of an O ring 36. By so configuring, when a compressor is stopped, it is possible to suppress striking sound (noise) generated when the balancer 35b abuts on the columnar portion 25a.

Description

  The present invention relates to a scroll compressor.

  2. Description of the Related Art Conventionally, a scroll compressor having a swing link mechanism that changes a turning radius (revolution radius) of a movable scroll is known. In the scroll compressor, the swing link mechanism changes the turning radius of the movable scroll by the compression reaction force of the fluid compressed in the working chamber, so that the movable side tooth portion of the movable scroll becomes the fixed side tooth portion of the fixed scroll. It functions to improve the sealing performance of the working chamber by pressing.

  For example, in Patent Document 1, as a swing link mechanism of this type, an eccentric portion provided on a rotating shaft is rotatably inserted into an insertion hole formed in a bush (cylindrical member) with a balancer. An apparatus is disclosed in which the revolution radius of the movable scroll is changed by inserting the outer peripheral side into a mounting hole formed in the movable scroll and further rotating the bush around the eccentric portion.

  Furthermore, in the swing link mechanism of Patent Document 1, a metal pin fixed to the bush and protruding in the direction of the rotation axis is inserted into a limit hole formed on the rotation axis and having an inner diameter larger than the outer diameter of the pin. doing. When the bush rotates around the eccentric portion, the bush and the balancer are prevented from being unnecessarily displaced around the eccentric portion by bringing the pin into contact with the inner peripheral wall surface of the limit hole.

  For this reason, in the swing link mechanism of Patent Document 1, when the scroll compressor starts and stops, the pin may collide with the inner peripheral wall surface of the limit hole and generate a hitting sound. Such a hitting sound becomes annoying noise for the user. Therefore, in the swing link mechanism of Patent Document 1, a hitting sound (noise) is suppressed by winding a buffer member made of a rubber material around a pin.

JP 2008-138865 A

  However, in the configuration in which the buffer member is arranged around the pin as in the swing link mechanism of Patent Document 1, only a small amount of the buffer member can be arranged. For this reason, a buffer member tends to deteriorate by collision. Furthermore, after the buffer member is deteriorated, it becomes impossible to suppress the hitting sound (noise).

  As a means for solving this problem, a means for arranging a sufficient amount of buffer member around the pin can be considered, but in order to arrange a sufficient amount of buffer member, the volume of the limit hole must be enlarged. . For this reason, the rotating shaft in which the limit hole is formed is increased in size, which causes an increase in the size of the scroll type compressor as a whole.

  An object of this invention is to suppress the noise of a scroll compressor, without enlarging in view of the said point.

The present invention has been devised to achieve the above object. In the invention according to claim 1, the columnar portion (25a) and the central axis (C0) extending coaxially with respect to the central axis (C0). A rotating shaft (25) having an eccentric portion (25b) arranged eccentrically with respect to the shaft, and a revolving motion by a rotational driving force transmitted from the rotating shaft (25), and a spiral movable side tooth portion (21b) A fixed scroll (22) having a scroll-like fixed side tooth portion (22b) meshing with the movable side tooth portion (21b), and an insertion hole (35c) into which the eccentric portion (25b) is inserted. ) Formed on the outer periphery of the cylindrical member (35a) and the cylindrical member (35a) when the cylindrical member (35a) rotates around the eccentric portion (25b). Member for contact with the outer peripheral surface of And 35b), with a,
When viewed from the axial direction of the central axis (C0), the center (C1) of the insertion hole (35c) is formed at a position eccentric to the center (C2) of the cylindrical member (35a) and is movable. A mounting hole (21c) into which the outer peripheral side of the cylindrical member (35a) is inserted is formed at the center of the scroll (21), and the cylindrical member (35a) rotates around the eccentric portion (25b). Further, when the abutting member (35b) and the columnar portion (25a) abut, the rotational displacement of the cylindrical member (35a) is restricted,
Further, at least one of the abutting member (35b) and the columnar portion (25a) is provided with a buffer member (36, 36a to 36) for reducing the impact when the abutting member (35b) and the columnar portion (25a) abut. Features a scroll compressor in which 36c) is arranged.

  According to this, the insertion hole (35c) into which the eccentric portion (25b) is inserted is formed at a position eccentric with respect to the center of the cylindrical member (35a), and is formed at the center portion of the movable scroll (21). The outer peripheral side of the cylindrical member (35a) is inserted into the mounting hole (21c). Therefore, the turning radius (revolution radius) from the central axis (C0) to the center of the movable scroll (21) can be changed by rotating the cylindrical member (35a) around the eccentric portion (25b). That is, a scroll compressor having a swing link mechanism is realized.

  Further, the contact member (35b) is fixed to the outer peripheral side of the cylindrical member (35a), and this contact member (35b) is brought into contact with the outer peripheral surface of the columnar portion (25a) of the rotating shaft (25). This restricts the rotational displacement of the cylindrical member (35a). Therefore, the contact portion between the contact member (35b) and the rotation shaft (25) can be positioned on the outer peripheral side of the rotation shaft (25), and it is easy to secure a space for arranging the buffer members (36... 36c). Become.

  As a result, a sufficient amount of the buffer member (36... 36c) can be disposed on at least one of the contact member (35b) and the columnar part (25a) without increasing the size of the scroll compressor as a whole. It is possible to suppress the deterioration of the buffer members (36... 36c). That is, according to the invention described in this claim, in the scroll compressor, noise generated by having the swing link mechanism can be suppressed without increasing the size.

  In the present claims, “the contact member (35b) and the columnar portion (25a) abut” is limited to the meaning that the contact member (35b) and the columnar portion (25a) are in direct contact. It is not intended to include the meaning that the abutting member (35b) and the columnar part (25a) abut indirectly via the buffer member (36... 36c).

  Further, in the scroll compressor having the above characteristics, the contact member (35b) may also have a function as a weight that suppresses unbalance of centrifugal force acting when the rotating shaft (25) rotates. . Thereby, the vibration and noise which arise by the unstable rotation of a rotating shaft (25) can be suppressed.

  Further, in the scroll compressor having the above characteristics, when viewed from the radial direction perpendicular to the central axis (C0), at least a part of the contact member (35b) and the columnar part (25a) are overlapped with each other. It may be arranged. Thereby, the structure which contact | abuts the member for contact (35b) and the outer peripheral surface of a columnar part (25a) is easily realizable.

  In the scroll compressor having the above characteristics, the columnar portion (25a) has a circular vertical cross section in the axial direction, and an annular groove (with a buffer member fitted in the outer peripheral surface of the columnar portion (25a)). 25d) may be formed, and an O-ring (36) may be employed as the buffer member. Thereby, the noise of a scroll compressor can be suppressed, suppressing the increase in manufacturing cost.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is an axial sectional view of the compressor of a 1st embodiment. It is an enlarged view of the X section of FIG. It is explanatory drawing which shows the positional relationship of the shaft of 1st Embodiment, and a balancer integrated bush. It is explanatory drawing which shows another positional relationship of the shaft of 1st Embodiment, and a balancer integrated bush. It is explanatory drawing for demonstrating arrangement | positioning of the buffer member of 2nd Embodiment. It is explanatory drawing for demonstrating arrangement | positioning of the buffer member of 3rd Embodiment. It is explanatory drawing for demonstrating arrangement | positioning of the buffer member of 4th Embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. 1-4. The scroll compressor 1 of the present embodiment (hereinafter simply referred to as the compressor 1) is applied to a vapor compression refrigeration cycle that adjusts the temperature of blown air that is blown into a vehicle interior by a vehicle air conditioner. In this refrigeration cycle, the refrigerant is compressed and discharged.

  The refrigeration cycle includes a condenser that exchanges heat between the high-pressure refrigerant discharged from the compressor 1 and the outside air to dissipate the high-pressure refrigerant, an expansion valve that decompresses the refrigerant that dissipated heat in the condenser, and a low pressure that is decompressed by the expansion valve. It is configured by connecting an evaporator that evaporates low-pressure refrigerant by exchanging heat between the refrigerant and the blown air, and a compressor 1 and the like in an annular manner via a refrigerant pipe or the like.

  In this refrigeration cycle, an HFC refrigerant (specifically, R134a) is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. Of course, an HFO refrigerant (for example, R1234yf) or the like may be adopted as the refrigerant. Furthermore, the refrigerant is mixed with refrigerating machine oil (oil) for lubricating the sliding portion in the compressor 1, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  Next, a detailed configuration of the compressor 1 will be described. The compressor 1 of this embodiment is arrange | positioned in the engine room of a vehicle, and is comprised as an electric compressor which operate | moves by supplying electric power.

  More specifically, as shown in FIG. 1, the compressor 1 includes a scroll-type compression mechanism 20 (hereinafter simply referred to as a compression mechanism 20), a compression mechanism inside a housing 10 that forms an outer shell thereof. An electric motor 30 that rotationally drives the motor 20 and a shaft 25 as a rotating shaft that transmits the rotational driving force from the electric motor 30 to the compression mechanism 20 are accommodated.

  In addition, the up and down arrows in FIG. 1 indicate the up and down directions in a state where the compressor 1 is applied to the vehicle air conditioner (mounted on the vehicle). Therefore, the compressor 1 of this embodiment is configured as a so-called horizontal type in which the rotation axis of the shaft 25 extends in the horizontal direction and the compression mechanism 20 and the electric motor 30 are arranged in the horizontal direction.

  The housing 10 has a closed container structure configured by combining a plurality of metal members. More specifically, the housing 10 of this embodiment includes a bottomed cylindrical (cup-shaped) front housing 11, a middle housing 12 that is disposed inside the front housing 11 and defines an internal space of the housing 10, and the front housing 11 includes a rear housing 13 that closes the opening side.

  The front housing 11, the middle housing 12, and the rear housing 13 are integrated by means such as press fitting or bolt fastening. In addition, a seal member made of an O-ring, a gasket, or the like is interposed in the contact portion where the front housing 11, the middle housing 12, and the rear housing 13 are in contact with each other, so that refrigerant does not leak from each contact portion. .

  A suction port 11b for sucking low-pressure refrigerant (specifically, low-pressure refrigerant flowing out of the evaporator of the refrigeration cycle) from the outside of the housing 10 is formed on the bottom surface portion 11a that forms one axial end side of the front housing 11. ing. The suction port 11b communicates with a motor side space 11c that houses the electric motor 30, and the low-pressure refrigerant sucked from the suction port 11b flows into the motor side space 11c.

  Further, a flat surface extending in a substantially horizontal direction is formed on the outer peripheral side surface of the cylindrical portion of the front housing 11, and a drive circuit 30 a for supplying electric power to the electric motor 30 is attached to the flat surface. . Therefore, in the compressor 1 of this embodiment, the electric motor 30 and the drive circuit 30a can be cooled by the low-pressure refrigerant that has flowed into the motor-side space 11c from the suction port 11b.

  The electric motor 30 is disposed on the inner peripheral side of the cylindrical portion of the front housing 11 and outputs a rotational driving force for driving the compression mechanism 20. More specifically, the electric motor 30 includes a stator 31 that forms a stator and a rotor 32 that forms a rotor.

  The stator 31 is fixed to the inner peripheral side surface of the cylindrical portion of the front housing 11, and includes a stator core 31a made of a magnetic material and a stator coil 31b wound around the stator core 31a. When electric power is supplied from the drive circuit 30a to the stator coil 31b, a rotating magnetic field that rotates the rotor 32 is generated.

  The rotor 32 includes a permanent magnet and is disposed on the inner peripheral side of the stator 31. Further, the rotor 32 is formed in a cylindrical shape extending in the rotation axis direction, and a columnar portion 25a of a metal shaft 25 is fixed to the shaft center hole of the rotor 32 by press-fitting.

  The shaft 25 includes a substantially columnar columnar portion 25a extending coaxially with respect to the central axis C0 (rotation central axis of the shaft 25), and an eccentric portion 25b arranged eccentrically with respect to the central axis C0. Has been. The eccentric portion 25b is formed in a substantially cylindrical shape extending in parallel with the central axis C0.

  Further, the columnar portion 25 a of the shaft 25 is formed to have a longer axial length than the rotor 32, and the end of the columnar portion 25 a on the one end side in the axial direction is substantially at the center of the bottom surface portion 11 a of the front housing 11. It is rotatably supported by the arranged motor side bearing 26a. On the other hand, the other axial end side (compression mechanism 20 side) of the columnar part 25a is rotatably supported by a compression mechanism side bearing 26b disposed at a substantially central part of the middle housing 12 formed in a substantially disc shape. Yes.

  Therefore, when electric power is supplied to the stator coil 31b and a rotating magnetic field is generated, the rotor 32 and the shaft 25 rotate together. The outer peripheral side surface of the middle housing 12 is press-fitted into the inner peripheral side surface of the cylindrical portion of the front housing 11, and the motor side space 11 c in which the electric motor 30 is accommodated and the compression mechanism 20 are accommodated in the internal space of the housing 10. The compression mechanism side space is partitioned.

  The compression mechanism 20 is a movable scroll 21 formed of metal (for example, aluminum alloy) as a pair of scrolls each having a flat plate portion and a spiral tooth portion protruding from the substrate portion in the axial direction of the shaft 25. And a fixed scroll 22.

  The movable scroll 21 has a disk-shaped movable side substrate portion 21a and a spiral movable side tooth portion 21b protruding from the movable side substrate portion 21a toward the fixed scroll 22 side. The fixed scroll 22 has a disk-shaped fixed side substrate portion 22a and a spiral fixed side tooth portion 22b protruding from the fixed side substrate portion 22a toward the movable scroll 21 side.

  Further, the fixed scroll 22 is fixed to the front housing 11 by pressing the outer peripheral side surface of the fixed side substrate portion 22 a into the inner peripheral side surface of the cylindrical portion of the front housing 11. The movable scroll 21 is disposed in a space formed between the middle housing 12 and the fixed scroll 22.

  The movable scroll 21 and the fixed scroll 22 are disposed so that the plate surfaces of the respective substrate portions 21a and 22a face each other, and the respective tooth portions 21b and 22b are engaged with each other, so that the tooth portion of one scroll is engaged. The tip portion is disposed so as to contact the substrate portion of the other scroll.

  Thereby, each tooth | gear part 21b and 22b contact in multiple places, and between each tooth | gear part 21b and 22b, when it sees from a rotating shaft direction, the working chamber V formed in a crescent moon shape is plurality. Individually formed. In FIG. 1, for clarity of illustration, only one of the plurality of working chambers V is given a reference numeral, and the other working chambers are omitted.

  As described above, the eccentric portion 25 b that is eccentric with respect to the rotation center of the shaft 25 is formed at the end of the shaft 25 on the other axial end side (compression mechanism 20 side). The eccentric portion 25b is rotated in a mounting hole 21c formed in the center portion of the surface on the middle housing 12 side of the movable side substrate portion 21a of the movable scroll 21 via the balancer-integrated bush 35 and the eccentric portion side bearing 26c. Inserted as possible.

  The balancer-integrated bush 35 is made of metal, and as shown in the enlarged view of FIG. 2 and the explanatory views of FIGS. 3 and 4, the bush 35a formed in a substantially cylindrical shape, and the outer periphery of the bush 35a. It has a balancer 35b formed in a substantially fan shape extending in a radial direction perpendicular to the central axis C0.

  3 and 4, the front view of the balancer-integrated bush 35 viewed from the electric motor 30 side in the axial direction of the central axis C0 is shown by a solid line, and two columnar portions 25a of the shaft 25 are shown. It is shown with a chain line.

  More specifically, an insertion hole 35c into which the eccentric portion 25b of the shaft 25 is rotatably inserted is formed in the bush 35a. The center C1 of the insertion hole 35c is formed at a position eccentric with respect to the center C2 of the bush 35a when viewed from the axial direction of the central axis C0. Furthermore, the outer peripheral side of the bush 35a is rotatably supported by an eccentric portion side bearing 26c fixed to the mounting hole 21c of the movable scroll 21, as shown in FIG.

  In the present embodiment, rolling bearings are employed as the eccentric portion side bearings 26c and the motor side bearings 26a and the compression mechanism side bearings 26b described above, but sliding bearings may be employed.

  As shown in FIGS. 3 and 4, the balancer 35b extends from the outer peripheral side of the bush 35a to the outer peripheral side of the columnar portion 25a of the shaft 25 when viewed from the axial direction of the central axis C0. Further, as shown in FIG. 2, a part of the balancer 35b is disposed so as to protrude toward the electric motor 30 and overlap with the columnar portion 25a of the shaft 25 when viewed from the radial direction perpendicular to the central axis C0. ing.

  Thereby, when the bush 35a rotates around the eccentric portion 25b, the inner peripheral side surface of the balancer 35b abuts on the outer peripheral surface side of the columnar portion 25a, and the balancer-integrated bush 35 rotates unnecessarily around the eccentric portion 25a. Displacement is regulated.

  As is clear from the above description, the bush 35a of the present embodiment constitutes a cylindrical member described in the claims, and the balancer 35b is a contact member described in the claims. Is configured. Furthermore, the balancer 35b of the present embodiment also has a function as a weight that suppresses unbalance of centrifugal force acting when the shaft 25 rotates.

  Further, as shown in FIG. 2, an annular groove 25d is formed on the outer peripheral surface of the columnar portion 25a of the shaft 25 so as to be continuous over the entire circumference. The groove 25d includes a balancer 35b and An O-ring 36 is fitted as a cushioning member that relieves an impact when the columnar portion 25a abuts.

  Therefore, in this embodiment, when the bush 35a rotates around the eccentric portion 25b, the inner peripheral side surface of the balancer 35b and the outer peripheral surface of the columnar portion 25a come into contact with each other via the O-ring 36. As the O-ring 36, it is desirable to employ a material that is formed of a material that is excellent in heat resistance and excellent in corrosion resistance against refrigerants and refrigerating machine oil. Therefore, in the present embodiment, those formed of HNBR (hydrogenated nitrile rubber) are employed.

  Further, as shown in FIG. 1, an anti-rotation mechanism 27 that prevents the movable scroll 21 from rotating around the bush 35 a of the balancer-integrated bush 35 is provided between the movable scroll 21 and the middle housing 12. Yes. Therefore, when the shaft 25 rotates, the movable scroll 21 turns (revolves) with respect to the fixed scroll 22 around the center axis C0 without rotating around the bush 35a.

  And by this revolving motion, the working chamber V mentioned above is displaced from the outer peripheral side to the center side around the rotation axis while reducing the volume. In this embodiment, a pin-hole type is adopted as the rotation prevention mechanism 27, but other types (for example, Oldham ring type) may be adopted.

  Further, the middle housing 12 of the present embodiment is formed with a suction-side communication passage (not shown) that connects the working chamber V that is displaced to the outermost peripheral side and has the maximum volume and the motor-side space 11c.

  A discharge hole 22c for discharging the refrigerant compressed in the working chamber V is formed at the center of the fixed-side substrate portion 22a of the fixed scroll 22. The discharge hole 22c communicates with the discharge chamber 13a into which the high-pressure refrigerant compressed in the working chamber V flows. In the discharge chamber 13a, the refrigerant passes from the discharge chamber 13a side to the working chamber V side via the discharge hole 22c. A reed valve 28 is provided to prevent backflow.

  The discharge chamber 13 a is formed by a space between the fixed scroll 22 and the rear housing 13, and the refrigerant outlet of the discharge chamber 13 a communicates with an oil separator 40 formed inside the rear housing 13.

  The oil separator 40 functions to separate the refrigerating machine oil from the high-pressure refrigerant compressed by the compression mechanism 20. More specifically, the oil separator 40 is configured by disposing a pipe member 40b having a smaller diameter than the columnar space in a columnar space 40a formed in the rear housing 13 and extending in the vertical direction (vertical direction). It is configured.

  In the oil separator 40, the high-pressure refrigerant containing the refrigerating machine oil flowing into the cylindrical space 40a from the discharge chamber 13a is swirled around the pipe member 40b, and the refrigerant and the refrigerating machine oil are separated by the action of centrifugal force. Yes.

  The refrigerating machine oil separated by the oil separator 40 is guided to the sliding portion of the compression mechanism 20 and the electric motor 30 through the oil passage 40c formed in the rear housing 13, the fixed scroll 22, the middle housing 12, and the like. . On the other hand, the high-pressure refrigerant separated by the oil separator 40 is guided to a discharge port 13 b that is formed in the rear housing 13 and discharges the high-pressure refrigerant to the outside of the housing 10.

  Next, the operation of the compressor 1 of the present embodiment having the above configuration will be described. When electric power is supplied to the electric motor 30 and the rotor 32 and the shaft 25 rotate, the movable scroll 21 turns (revolves) with respect to the fixed scroll 22. Thereby, the working chamber V of the compression mechanism 20 is displaced from the outer peripheral side to the center side while reducing the volume.

  Here, since the working chamber V formed on the outermost peripheral side and having the maximum volume communicates with the motor side space 11c, the low-pressure refrigerant flowing into the motor side space 11c from the suction port 11b has the maximum volume. Is sucked into the working chamber V. At this time, the low-temperature low-pressure refrigerant flows in the motor-side space 11 c, thereby cooling the electric motor 30 and cooling the drive circuit 30 a via the wall surface of the front housing 11.

  Then, the refrigerant in the working chamber V is compressed by the displacement of the working chamber V from the outer peripheral side to the center side while reducing the volume. Furthermore, when the working chamber V is displaced toward the center and the refrigerant pressure in the working chamber V exceeds the opening pressure of the reed valve 28, the reed valve 28 is opened, and the high-pressure refrigerant in the working chamber V passes through the discharge hole 22c. Flow into the discharge chamber 13a. The high-pressure refrigerant flowing out from the discharge chamber 13a is separated from the refrigerating machine oil by the oil separator 40 and discharged from the discharge port 13b.

  As described above, according to the compressor 1 of the present embodiment, the refrigerant can be sucked, compressed and discharged in the refrigeration cycle.

  Further, in the compressor 1 according to the present embodiment, the center C1 of the insertion hole 35c formed in the balancer-integrated bush 35 is formed at a position eccentric with respect to the center C2 of the bush 35a, and the outer peripheral side of the bush 35a is movable. The eccentric part bearing 26c fixed to the scroll 21 is rotatably supported.

  Therefore, the turning radius of the movable scroll 21 can be changed from the shaft 25 by rotating the bush 35 a around the shaft 25. That is, in this embodiment, the swing link mechanism can be configured by the balancer-integrated bush 35. The swing link mechanism is sometimes called a driven crank mechanism.

  Thereby, for example, in a state where the compressor 1 is operating, the bush 35a is caused to turn the turning radius of the movable scroll 21 (in FIG. 3 by the compression reaction force of the refrigerant in the working chamber V as shown in FIG. 3). Rotate to the side of increasing R1). Thereby, the outer peripheral side surface of the movable side tooth portion 21 b of the movable scroll 21 can be pressed against the inner peripheral side surface of the fixed side tooth portion 22 b of the fixed scroll 22.

  Then, when the compressor 1 is stopped from this state (that is, when the rotation of the shaft 25 is stopped), the compression reaction force of the refrigerant in the working chamber V decreases and the inertial force acting on the balancer-integrated bush 35. 4, the balancer 35b is displaced so as to contact the columnar portion 25a of the shaft 25, as shown in FIG. Thereby, the turning radius (R2 in FIG. 4) of the movable scroll 21 becomes smaller than that when the compressor 1 is operated.

  As described above, in the compressor 1 of the present embodiment, a swing link mechanism can be configured, and the airtightness (sealability) of the working chamber V can be improved when the compressor 1 is operated. The dimensional difference between the orbiting scroll radius (R1 in FIG. 3) when the compressor 1 is operating and the orbiting scroll radius (R2 in FIG. 4) when the compressor 1 is stopped is extremely large. In fact, the difference is about several tens of microns to several hundreds of microns.

  Here, in the swing link mechanism of the present embodiment, when the compressor 1 is stopped, the balancer 35b of the balancer-integrated bush 35 comes into contact with the columnar portion 25a of the shaft 25, so that the balancer 35b and the columnar portion 25a collide. The hitting sound may become annoying noise for the user (occupant).

  On the other hand, in this embodiment, the O-ring 36 serving as a buffer member is disposed between the balancer 35b and the columnar portion 25a, and the balancer 35b and the columnar portion 25a are brought into contact with each other via the buffer member. The hitting sound (noise) at the time of contact can be suppressed.

  Further, in the present embodiment, the balancer 35b is disposed in a range from the outer peripheral side of the bush 35a to the outer peripheral side of the columnar portion 25a, and the inner peripheral surface side of the balancer 35b is brought into contact with the outer peripheral surface of the columnar portion 25a. ing. Therefore, the contact portion between the balancer 35b and the shaft 25 can be positioned on the outer peripheral side of the shaft 25, and it is easy to secure a space for arranging the buffer member (O-ring 36).

  As a result, a sufficient amount of the buffer member can be disposed on the outer peripheral side of the shaft 25 without increasing the size of the scroll compressor 1 as a whole, and deterioration of the buffer member (O-ring 36) can be suppressed. That is, according to the scroll compressor 1 of the present embodiment, it is possible to suppress noise generated by having the swing link mechanism without increasing the size.

  In the present embodiment, the effect of suppressing the hitting sound (noise) between the balancer 35b and the columnar portion 25a when the compressor 1 is stopped has been described. Of course, the balancer 35b hits the columnar portion 25a during startup. Even in a compressor configured to be in contact with each other, it is possible to similarly suppress the hitting sound at the time of contact between the balancer 35b and the columnar portion 25a.

  Moreover, according to the compressor 1 of this embodiment, since the balancer 35b has a function as a weight which suppresses the unbalance of the centrifugal force which acts when the shaft 25 rotates, the shaft 25 is unstable. Vibration and noise caused by rotation can be suppressed.

Further, according to the compressor 1 of the present embodiment, when viewed from the radial direction of the central axis C0, the balancer 35b and the columnar portion 25a are arranged so that at least a part thereof is polymerized,
A configuration in which the balancer 35b and the outer peripheral surface of the columnar portion 25a are brought into contact with each other can be easily realized.

  Further, according to the compressor 1 of the present embodiment, an annular groove is formed on the outer peripheral surface of the columnar portion 25a whose axial vertical cross section is formed in a circular shape, and an O-ring is provided as a buffer member in the groove 25d. It is inserted. That is, since a relatively inexpensive O-ring is employed as the buffer member, noise of the compressor 1 can be suppressed while suppressing an increase in manufacturing cost of the compressor 1 as a whole.

  Further, the compressor 1 of the present embodiment is configured as an electric compressor including an electric motor 30. Therefore, the compressor from the engine, such as an electric vehicle that obtains driving force for traveling from the electric motor for traveling, or a hybrid vehicle that obtains driving force for traveling from both the traveling electric motor and the internal combustion engine (engine). Even when applied to a vehicle in which the driving force for driving the vehicle cannot be stably obtained, stable boosting performance can be exhibited.

  Furthermore, if noise generated by having the above-described swing link mechanism occurs when no engine operating sound is generated, this hitting sound is likely to be heard by the user (occupant). Therefore, the noise suppression effect of the compressor 1 of the present embodiment is effective in an electric compressor mounted on an electric vehicle or a hybrid vehicle.

(Second to fourth embodiments)
In 1st Embodiment, although the example which has arrange | positioned O ring 36 which is a buffer member in the columnar part 25a of the shaft 25 was demonstrated, as shown in the explanatory drawing of FIGS. 5-7 in 2nd-4th embodiment. An example in which the buffer members 36a to 36c are arranged on the balancer 35b of the balancer-integrated bush 35 will be described.

  5 to 7 are drawings corresponding to FIG. 3 of the first embodiment, and the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals. The same applies to the following drawings. 5 to 7 schematically show positions where the buffer members 36a to 36c are arranged. More specifically, when the balancer-integrated bush 35 is seen transparently from the axial direction, the range occupied by the buffer member is shown by being filled.

  First, the buffer member 36a of 2nd Embodiment is arrange | positioned in the whole area of the inner peripheral surface side which opposes the outer peripheral surface of the columnar part 25a among the balancers 35b. More specifically, the buffer member 36a is fixed to the balancer 35b by being fitted into a groove formed on the inner peripheral surface of the balancer 35b. Of course, the buffer member 36a may be fixed to the inner peripheral surface of the balancer 35b by bonding means such as adhesion or welding. Other configurations and operations are the same as those in the first embodiment.

  Therefore, the compressor 1 of this embodiment can also obtain the same effect as that of the first embodiment. Furthermore, since the buffer member 36a of this embodiment is pressed to the outer peripheral side by the action of centrifugal force during the operation of the compressor 1, it is difficult to come off from the groove formed on the inner peripheral surface of the balancer 35b.

  Moreover, as shown in FIG. 5, you may provide the nail | claw part latched by the engaging part formed in the circumferential direction side surface of the balancer in the circumferential direction both ends of the buffer member 36a. This facilitates alignment when attaching the buffer member 36a to the balancer 35b.

  In the third embodiment, as a modification of the second embodiment, as shown in the explanatory view of FIG. 6, when viewed from the axial direction of the central axis C0, the buffer member 36b is extended over the entire circumference of the balancer 35b. It is arranged.

  As such a buffer member 36b, a modified O-ring can be adopted. Further, the buffer member 36b may be fixed to the balancer 35b by being fitted into a groove formed over the entire circumference of the balancer 35b, or may be fixed to the balancer 35b by bonding means such as adhesion or welding. Also good.

  In the fourth embodiment, as a modification of the second embodiment, as shown in the explanatory view of FIG. 7, a buffer member 36 c is arranged at the contact portion of the balancer 35 b with the columnar portion 25 a of the shaft 25 and its peripheral portion. doing.

  Such a buffer member 36c has a poppet shape (mushroom shape) having a flat portion interposed at a contact portion between the balancer 35b and the columnar portion 25a and a column portion extending from the flat portion toward the balancer 35b. Can be adopted. Further, the buffer member 36c may be fixed to the balancer 35b by fitting the column portion into a fixing hole formed in the balancer 35b, or may be fixed to the balancer 35b by bonding means such as adhesion or welding. Good.

  As described above, by providing the buffer members 36a to 36c at least on the portion of the outer surface of the balancer 35b that contacts the columnar portion 25a, noise generated by having the swing link mechanism as in the first embodiment. Can be suppressed. The buffer members 36a to 365c may be formed integrally with the balancer-integrated bush 35 by means such as insert molding.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, the example in which the compressor 1 according to the present invention is applied to the refrigeration cycle of the vehicle air conditioner has been described. However, the application of the compressor according to the present invention is not limited to this. That is, the compressor according to the present invention can be applied to a wide range of uses as a compressor that compresses various fluids.

  (2) In the above-described embodiment, the example in which the compressor 1 according to the present invention is configured as an electric compressor has been described. For example, the rotational driving force from the internal combustion engine (engine) via a pulley with a clutch, a belt, and the like. May be configured as an engine-driven compressor to which is transmitted.

  Further, in a compressor that is engine-driven and whose discharge capacity is adjusted by the engagement / disengagement of the clutch regardless of the engine speed, the frequency of operation and stop of the compressor increases in order to adjust the discharge capacity. Therefore, the noise suppression effect of the compressor according to the present invention is also effective in an engine-driven compressor.

  (3) In the above-described embodiment, an example in which the bush 35a constituting the cylindrical member and the balancer 35b constituting the contact member are integrally formed as the balancer-integrated bush 35 has been described. 35b may be formed as a separate member and integrated by means such as press-fitting and adhesion.

  (4) In the above-described embodiment, the buffer member formed of HNBR is used, but the material of the buffer member is not limited to this. For example, EPDM (ethylene propylene diene rubber), which is a rubber material that is excellent in heat resistance and excellent in corrosion resistance against refrigerants and refrigerating machine oil, may be employed.

  Furthermore, PTFE (tetrafluoroethylene), PEN (polyethylene naphthalate), PA (polyamide), PET (polyethylene terephthalate), etc., which are resin materials having similar properties as the buffer member, may be employed.

  (5) In the above-described first embodiment, the example in which the O-ring 36 is employed as the buffer member has been described. However, when the buffer member is disposed on the columnar portion 25a of the shaft 25, the second and fourth embodiments are also used. Similarly, you may arrange | position a buffer member in the one part range including the site | part which contact | abuts the balancer 35b among the outer peripheral surfaces of the columnar part 25a.

  That is, noise generated by having a swing link mechanism, as in the first embodiment, by fixing the buffer member to at least a portion of the outer surface of the columnar portion 25a of the shaft 25 where the balancer 35b abuts. Can be suppressed.

  The buffer member may be disposed on both the columnar portion 25a of the shaft 25 and the balancer 35b of the balancer-integrated bush 35.

25 Rotating shaft 25a Columnar portion 25b Eccentric portion 21 Movable scroll 22 Fixed scroll 35a Bush (cylindrical member)
35b Balancer (contact member)
35c Insertion hole 36, 36a-36c Buffer member

Claims (8)

A rotating shaft (25) having a columnar portion (25a) extending coaxially with respect to the central axis (C0) and an eccentric portion (25b) disposed eccentrically with respect to the central axis (C0);
A revolving motion by a rotational driving force transmitted from the rotary shaft (25), and a movable scroll (21) having a spiral movable side tooth portion (21b);
A fixed scroll (22) having a spiral fixed side tooth portion (22b) meshing with the movable side tooth portion (21b);
A cylindrical member (35a) having an insertion hole (35c) into which the eccentric part (25b) is inserted;
For abutting, which is fixed to the outer peripheral side of the cylindrical member (35a) and contacts the outer peripheral surface of the columnar part (25a) when the cylindrical member (35a) rotates around the eccentric part (25b). A member (35b),
When viewed from the axial direction of the central axis (C0), the center (C1) of the insertion hole (35c) is formed at a position eccentric to the center (C2) of the cylindrical member (35a). And
A mounting hole (21c) into which the outer peripheral side of the cylindrical member (35a) is inserted is formed at the center of the movable scroll (21).
When the cylindrical member (35a) rotates around the eccentric part (25b), the contact member (35b) and the columnar part (25a) come into contact with each other, so that the cylindrical member (35a) The rotational displacement is regulated,
At least one of the abutting member (35b) and the columnar portion (25a) is provided with a buffer member (36, 36) for reducing an impact when the abutting member (35b) and the columnar portion (25a) abut. 36a-36c) are arranged, and the scroll type compressor characterized by the above-mentioned.   The said abutting member (35b) has a function as a weight which suppresses the unbalance of the centrifugal force which acts when the said rotating shaft (25) rotates, The Claim 1 characterized by the above-mentioned. Scroll type compressor.   The contact member (35b) and the columnar part (25a) are arranged so as to overlap each other when viewed from a radial direction perpendicular to the central axis (C0). The scroll compressor according to claim 1 or 2. The columnar part (25a) has a vertical cross section in the axial direction formed in a circular shape,
An annular groove (25d) into which the buffer member is fitted is formed on the outer peripheral surface of the columnar part (25a),
The scroll compressor according to any one of claims 1 to 3, wherein the buffer member comprises an O-ring (36).   The buffer member (36) is fixed to at least a portion of the outer surface of the columnar portion (25a) where the contact member (35b) contacts. The scroll type compressor as described in any one.   The buffer member (36a to 36c) is fixed to at least a portion of the outer surface of the contact member (35b) that contacts the columnar portion (25a). A scroll compressor according to any one of the above.   The scroll compressor according to any one of claims 1 to 6, further comprising an electric motor (30) for outputting a rotational driving force for rotating the rotating shaft (25).   The scroll type compressor according to any one of claims 1 to 7, wherein the buffer member (36) is formed of hydrogenated nitrile rubber.

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