JP6637863B2 - Hermetic compressor and equipment equipped with it - Google Patents

Description

  The present invention relates to a hermetic compressor and a device equipped with the same.

It is a conventionally well-known problem to miniaturize devices such as a compressor.
In Patent Literature 1, a compressor element 13 is provided at an upper part, and a motor element 14 is provided at a lower part. A structure (frame) between the compressor element 13 and the motor element 14 is elastically supported by a spring-like material in the sealed container 12. The disclosed configuration is disclosed.

JP-A-62-147065

  Patent Document 1 can contribute to downsizing of the vertical dimension of the compressor by arranging the spring-like material extending in the vertical direction on the left and right sides instead of below the electric element or the like. However, when an object that appears to be a spring (elastic body) is connected below the electric element, vibrations generated from the compressor element and the electric motor element are generated by the vibration source (piston and cylinder), the frame, the stator of the electric motor element, and the elastic element. After traveling down the body, it travels to the sealed container 12. On the other hand, when a spring-like object is connected to the frame, the vibration is transmitted to the closed casing 12 without passing through the stator of the electric motor element. That is, as an object for attenuating the vibration, the influence exerted by the stator is eliminated, the vibration is hardly attenuated, and the influence of a configuration (frame or elastic body) other than the stator becomes relatively large. In order to attenuate the vibration, it is preferable to increase the mass and / or rigidity of the structure provided in the transmission path.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a hermetic compressor having a small vertical dimension and capable of reducing vibration.

The present invention in view of the above circumstances,
In a hermetic compressor including a compression element including a piston and a cylinder serving as a vibration source, an electric element that drives the compression element and includes a stator, a sealed container that houses the compression element and the electric element, and a frame. ,
The cylinder is disposed above the frame, the stator is disposed below the frame,
The frame is supported by the closed container via at least two elastic members provided on each of the compression element side and the opposite side of the compression element side ,
The elastic member is connected to a lower surface of the frame ,
The frame is connected to said elastic member, and wherein the projecting portion projecting downward, the Rukoto to have a, a protrusion upper projecting toward the upper case of the closed container.

  According to the present invention, it is possible to provide a hermetic compressor that is small and capable of reducing vibration.

It is a longitudinal section showing the hermetic compressor of this embodiment. It is a cross section showing the hermetic compressor of this embodiment. It is a schematic diagram explaining the effect of a closed type compressor, (a) is this embodiment, (b) is a comparative example. 1 is a schematic cross-sectional view of a refrigerator equipped with a hermetic compressor of the present embodiment, wherein (a) shows a configuration in which the hermetic compressor is arranged at the lower part of the refrigerator, and (b) shows a configuration in which the hermetic compressor is arranged on the upper part of the refrigerator. This is the configuration. 4 is a graph showing the relationship between the bearing loss and (bearing length / shaft diameter).

  Hereinafter, a hermetic compressor 100 according to an embodiment of the present invention will be described with reference to the accompanying drawings.

FIG. 1 is a longitudinal sectional view showing a hermetic compressor of the present embodiment.
As shown in FIG. 1, the hermetic compressor 100 is a so-called reciprocating compressor configured by arranging a compression element 20 and an electric element 30 in a closed container 3. The compression element 20 and the electric element 30 are elastically supported in the closed container 3 via a plurality of coil springs 9 (elastic members). In the closed container 3, an upper case 3m constituting a substantially upper half outer shell and a lower case 3n constituting a substantially lower half outer shell are joined by welding or the like, and a space for accommodating the compression element 20 and the electric element 30 therein is provided. Have.

  The compression element 20 includes a cylinder 21, a crankshaft 23 for compressing a refrigerant by reciprocating a piston 22 in the cylinder 21, and a radial bearing 25 for supporting the crankshaft 23. The radial bearing 25 (bearing) is formed integrally with the cylinder 21 and the frame 24. The crankshaft 23 is rotatably supported by a frame 24 via a thrust bearing 26.

  The frame 24 has a base 24a extending in a substantially horizontal direction. The cylinder 21 is located above the base 24a. On the lower surface side of the base 24a, a protruding portion 24e connected to the coil spring 9 protrudes downward, and is formed integrally with the base 24a. For the base 24a, for example, cast iron such as FC200 can be adopted. On the upper surface side of the base 24a, an upper protrusion 24u protruding toward the upper case 3m is formed integrally with the base 24a. The upper protruding portion 24u may protrude to a position substantially equal to or higher than the upper end of the crankshaft 23 or the upper end of the cylinder 21, for example. In this way, the area of the frame 24 is expanded, and the mass is secured. The thickness (vertical dimension) of the frame 24 is preferably thicker from the viewpoint of mass, and is preferably uniform over the entire area from the viewpoint of rigidity. According to the inventor's trial, for example, a preferable balance can be obtained when the thinnest portion is 11 mm or more and the thickest portion is 23 mm or less.

  In addition, a cylindrical radial bearing 25 that extends vertically downward (toward the bottom surface of the lower case 3n) is formed at a substantially central portion of the frame 24. Further, the frame 24 forms a part of the cylinder 21.

  The cylinder 21 is formed at a position deviated radially outward from the center axis O of the crankshaft 23. A head cover 27 is attached to an end of the cylinder 21 on the outer peripheral side in the axial direction, and a piston 22 is inserted into an end on the opposite side. Thus, the compression chamber (cylinder chamber) Q1 is constituted by the cylinder 21, the head cover 27, and the piston 22. In addition, between the cylinder 21 and the head cover 27, a valve opening / closing mechanism provided with an intake valve that opens when the refrigerant is sucked and a discharge valve that opens when the compressed refrigerant is discharged is provided.

  The radial bearing 25 is constituted by a slide bearing on which the crankshaft 23 is supported. Further, the radial bearing 25 is constituted by a through hole 24 b formed in the frame 24. The thrust bearing 26 is disposed in a concave portion 24c formed in a circular groove shape around the through hole 24b on the upper surface of the base 24a.

  The large-diameter end 22b of the connecting rod 22a is connected to a crank pin 23a described later, and the small-diameter end 22c of the connecting rod 22a is connected to the piston 22 via a pin 22d.

  A crankpin 23 a is formed at the upper end of the crankshaft 23, and the crankpin 23 a is formed at a position eccentric from the rotation center axis O of the crankshaft 23. The lower end of the crankshaft 23 is located near the lower case 3n. When the crank pin 23a rotates eccentrically with respect to the rotation center axis O, the piston 22 reciprocates in the cylinder 21.

  Further, the crankshaft 23 has a flange portion 23b extending in a direction (horizontal direction) orthogonal to the rotation center axis O above the through hole 24b.

  The crankshaft 23 is formed with a hollow hole 23c which is concave upward from the lower end in the axial direction, and has a hollow portion in the crankshaft 23. The crankshaft 23 has an upper communication hole 23d penetrating from the upper end of the center hole 23c to the upper surface of the flange portion 23b.

  A helical groove 23e is formed on the outer peripheral surface of the crankshaft 23 up to the vicinity of the flange portion 23b. The upper end of the helical groove 23e communicates with the concave pin hole 23f formed in the crank pin 23a through the pin communication hole 23g.

  A fixed shaft member 28 is inserted into a hollow portion of the crankshaft 23. The fixed shaft member 28 is fixed by a fixing tool (not shown) so as not to rotate even when the crankshaft 23 rotates. On the outer peripheral surface of the fixed shaft member 28, a fixed shaft spiral groove 28a is formed. A spiral lubricating oil passage is formed by the wall surface of the fixed shaft spiral groove 28a and the wall surface of the center hole 23c. As the wall surface moves due to the rotation of the crankshaft 23, the lubricating oil is dragged to the wall surface by viscous effect. The fixed shaft spiral groove 28a rises.

  The lubricating oil that has risen through the center hole 23c blows out onto the flange portion 23b through the upper communication hole 23d to lubricate the thrust bearing 26. The lubricating oil that has risen in the spiral groove 23e of the crankshaft 23 lubricates between the crankshaft 23 and the radial bearing 25, passes through the pin communication hole 23g, and passes through the pin hole 23f of the crank pin 23a. To lubricate the periphery of the connecting rod 22a. The lubricating oil that has lubricated the thrust bearing 26 and the like is configured to return to the bottom of the sealed container 3 via the hole 24s (see FIG. 2).

  The electric element 30 is disposed below the frame 24 (below the base 24 a), and includes a rotor 31 and a stator 32.

  The rotor 31 includes a rotor core formed by laminating electromagnetic steel sheets, and is fixed to a lower portion of the crankshaft 23 by press fitting or the like. The rotor 31 has a flat shape in which the radius R is larger than the thickness (height in the axial direction) T1. Further, the thickness (axial height) T1 of the rotor 31 is set to approximately half the length (bearing length) L of the radial bearing 25.

  The stator 32 is arranged on the outer periphery of the rotor 31, and is formed of an iron core 32 a including a cylindrical stator core and a plurality of slots formed on the inner circumference of the stator core, and wound around the iron core 32 a via an insulator (not shown). And a turned coil 32b. The iron core 32a has a flat shape in which the length L1 in the radial direction is longer than the thickness (height in the axial direction) T2 in the longitudinal sectional view of FIG. The coil 32b also has a flattened shape whose length in the radial direction is longer than its thickness (height in the axial direction) in the longitudinal sectional view of FIG. The thickness (axial height) T2 of the iron core 32a is configured to be substantially the same as the thickness (axial height) T1 of the rotor 31. As described above, when the rotor 31 is flattened, the torque for rotating the rotor 31 can be increased by expanding the diameter of the stator 32 to make it flat.

  The frame 24 provided with the compression element 20 and the electric element 30 in this manner is elastically supported via the plurality of coil springs 9 in the closed casing 3. The compression element 20 and the electric element 30 are designed in a state where a predetermined clearance CL is set in advance so that the compression element 20 and the electric element 30 do not come into contact with the inner wall surface of the closed container 3 when vibrating during operation.

  The coil spring 9 is provided on the side of the cylinder 21 (compressor chamber side Q2, left side in FIG. 1) which constitutes a part of the compression element 20 and on the side opposite to the side of the cylinder 21 (anti-compressor chamber side Q3, FIG. 1). (Right side). In the present embodiment, a total of four coil springs 9 are provided on the compression chamber side Q2 and the anti-compressor chamber side Q3, respectively, on the near side and the back side in a direction perpendicular to the plane of FIG. 2). All the coil springs 9 have the same shape and the same spring characteristics. In this way, by using a single type of the coil spring 9, it is possible to prevent an erroneous arrangement when the coil springs 9 are of different types. However, the number of coil springs 9 is not limited to four, but may be three or five or more.

  In addition, the frame 24 has an extension 24 d that extends outward (radially outward) from the cylinder 21. The extending portion 24d extends more outward than the stator 32. In addition, a protrusion 24e that fits and holds the upper part of the coil spring 9 is formed on the lower surface of the extension 24d.

  Further, the frame 24 also has an extension 24f extending to the same extent as the extension 24d on the side opposite to the extension 24d. The extension 24f also extends to the outer peripheral side of the stator 32. On the lower surface of the extension 24f, a projection 24g that fits and holds the upper part of the coil spring 9 is formed. On the bottom surface of the sealed container 3, a stepped portion 3 a that rises so as to protrude into the sealed container 3 is formed on the outer peripheral side of the stator 32. The step 3a is formed by combining a part of the bottom surface and a part of the side surface of the lower case 3n to form a concave shape. Further, at least a portion of the step portion 3 a overlaps with at least a portion of the coil spring 9 in a top view, and is provided at a position corresponding to the position of the coil spring 9. Further, a projection 3b is formed at the upper end of the step 3a to be fitted and held by the lower part of the coil spring 9. The protrusion 3b is located above the lower surface 31a of the rotor 31. The oil surface 40 of the lubricating oil is configured to be located below the lower surface 31a of the rotor 31 so that the rotor 31 is not immersed in the lubricating oil.

  FIG. 2 is a transverse sectional view showing the hermetic compressor of the present embodiment. In FIG. 2, the flow of the refrigerant in the hermetic compressor 100 will be described.

  As shown in FIG. 2, returning from the refrigerator 66 (see FIG. 4) of the refrigerator, the refrigerant introduced from the suction pipe 3e penetrating through the closed casing 3 is connected to the suction port (not shown) of the suction silencer 41. ), Is introduced into the compression chamber Q1 (see FIG. 1) via the head cover 27 and the like. Further, the refrigerant compressed by the piston 22 in the compression chamber Q1 passes through a discharge chamber space (not shown), passes through discharge silencers 42a and 42b formed in the frame 24 and a pipe 3f, and flows from a discharge pipe 3g to a cooler. 66 (see FIG. 4).

  3A and 3B are schematic diagrams illustrating the operation and effect of the hermetic compressor, wherein FIG. 3A is the present embodiment, and FIG. 3B is a comparative example.

  In the comparative example shown in FIG. 3B, the compression element 120 and the electric element 130 are arranged above and below the frame 124, and the electric element 130 is elastically supported in the closed casing 90 via the coil springs 90, 90. In this case, the center of gravity of the internal mechanism (the compression element 120 and the electric element 130) is located above the upper ends of the coil springs 90, 90, so that when vibrating in the double-headed arrow direction during operation, the deflection angle b increases. On the other hand, in the embodiment shown in FIG. 3A, the compression element 20 is arranged on the upper part of the frame 24, and the electric element 30 is arranged on the lower part, and the frame 24 is elastically inserted into the closed container 3 via the coil springs 9, 9. Supported. In this case, the compression element 20 and the electric element 30 vibrate in the directions indicated by double arrows, respectively, during operation. The angle a (<b) becomes smaller.

  As described above, in the hermetic compressor 100, the compression element 20 is disposed above the frame 24, and the electric element 30 is disposed below the frame 24, and the frame 24 is elastically supported. It becomes possible to reduce. Furthermore, by increasing the plate thickness of the frame 24 that transmits the vibration of the compression element 20 to the closed container 3 via the coil spring 9, the vibration of the internal mechanism can be more effectively suppressed.

  Further, in the embodiment, the vibration CL can be reduced by reducing the vibration as compared with the comparative example, so that the clearance CL between the internal mechanism (the compression element 20 and the electric element 30) and the closed casing 3 (see FIG. 1). ) Can be shortened. As a result, the size of the sealed container 3 can be reduced, and the size of the sealed compressor 100 can be reduced.

  Further, a rubber seat 10 for elastically supporting the closed container 3 is provided below each step 3a (see FIG. 1). The rubber seat 10 is supported by a plate 11 fixed to the lower case 3n of the closed container 3. Further, the rubber seat 10 is disposed at a position overlapping the coil spring 9 in the vertical direction (up and down direction).

  By forming the stepped portion 3a and disposing the coil spring 9 in the stepped portion 3a, the coil spring 9 can be installed at a height not immersed in the lubricating oil. This can prevent noise generated when vibrating in the compressor, and can make the hermetic compressor 100 quiet. In addition, by disposing the rubber seat 10 below the stepped portion 3a, the rubber seat 10 can be prevented from protruding greatly downward from the lower case 3n of the closed casing 3, so that the height of the hermetic compressor 100 is increased. And the size of the hermetic compressor 100 can be reduced.

  Incidentally, since heavy objects such as the cylinder 21 and the piston 22 are disposed in the compressor chamber side Q2, the weight becomes heavier than that in the non-compressor chamber side Q3 (the side opposite to the compressor chamber side), and the coil spring 9 is increased. That is, the load applied to the coil spring 9 on the compressor chamber side Q2 and the load applied to the coil spring 9 on the non-compressor chamber side Q3 have different values. In this case, for example, if the types of the coil springs 9 are the same, and the lower ends of the two coil springs 9 have the same height in contact with the lower ends of the coil springs 9, the sinking amount (shrinkage) Amount), and the internal mechanism (the compression element 20 and the electric element 30) is inclined in an initial state before the operation. A clearance (margin) is provided between the closed container 3 and the internal mechanism in consideration of vibration (tilt) during operation. However, if the heights of the abutting surfaces are the same, there is a possibility that the internal mechanism may collide with the inside of the sealed container 3, so that it is necessary to secure a large clearance, and the compressor becomes large.

  Therefore, in the present embodiment, the height h1 of the contact surface 3c with which the lower end of the coil spring 9 of the compressor chamber side Q2 (the cylinder 21 side, the left side in FIG. 1) to which more load is applied is relatively small. The lower end of the coil spring 9 on the compressor chamber side Q3 (the right side in FIG. 1) is configured to be higher than the height h2 of the contact surface 3d with which the coil spring 9 contacts. The difference between the height h1 of the contact surface 3c and the height h2 of the contact surface 3d is set to a value at which the internal mechanism is in a horizontal state in an initial state before operation when supported by the coil spring 9.

  As described above, in the hermetic-type compressor 100, by setting the height h1 of the contact surface 3c to be higher than the height h2 of the contact surface 3d, the internal mechanism is kept horizontal in the initial state before operation. Since the support can be performed in a state, the inclination of the internal mechanism during operation can be suppressed to a small value. As a result, the clearance CL (see FIG. 1) between the sealed container 3 and the internal mechanism can be set small, and the sealed compressor 100 can be reduced in size. By adjusting the contact surfaces 3c and 3d, all the coil springs 9 can be made of the same type (shape and characteristic), so that mistakes and the like can be prevented in the assembly process of the coil springs 9.

  Note that, instead of or in addition to adjusting the height of the contact surface 3c and the height of the contact surface 3d, the height of the lower surfaces of the extending portions 24d and 24f of the frame 24 is adjusted in the compressor chamber side Q2. The height position of the extension portion 24d may be higher than the height position of the extension portion 24f on the anti-compressor chamber side Q3. That is, the upper end position of the natural length of the coil spring 9 on the compressor chamber side Q2 where the load is large can be higher than the upper end position of the natural length of the coil spring 9 on the anti-compressor chamber side Q1 where the light load is small. . This also makes it possible to keep the inclination of the internal mechanism small.

  FIGS. 4A and 4B are schematic cross-sectional views of a refrigerator as an example of a device equipped with the hermetic compressor of the present embodiment. FIG. 4A shows a configuration in which the hermetic compressor is arranged at a lower portion, and FIG. In this configuration, the machine is arranged at the top.

  As shown in FIG. 4A, the refrigerator 60A is configured by dividing the refrigerator main body 61 into a plurality of storage rooms 62, 63, 64, and 65. For example, the storage room 62 is a refrigerator room, the storage room 63 is an upper freezer room, the storage room 64 is a lower freezer room, and the storage room 65 is a vegetable room. Note that the positional relationship between the storage chambers 62, 63, 64, and 65 is not limited to that shown in FIG. The hermetic compressor 100 is disposed in a machine room at the lower rear part of the drawer 65a of the storage chamber 65 (the lowermost lower end on the rear side of the refrigerator main body 61). The refrigerant discharged from the hermetic compressor 100 passes through a condenser (not shown) and a decompression mechanism (not shown) provided in the refrigerator 60A, absorbs the heat in the refrigerator by the cooler 66, and is sealed again. It is returned into the mold compressor 100.

  By the way, when a tall hermetic compressor is applied as in the related art, the capacity of the drawer 65a stored in the storage chamber 65 becomes small (shallow drawer) because it is necessary to increase the volume of the machine room. Therefore, by adopting the refrigerator 60A to which the hermetic compressor 100 of the present embodiment is applied, the volume of the machine room can be reduced, and the height position of the ceiling surface of the machine room can be reduced. , It is possible to increase the internal capacity on the back side of the container.

  Further, as shown in FIG. 4B, in the refrigerator 60B, the hermetic compressor 100 is arranged in a machine room at the upper rear part of the storage chamber 62 (the uppermost rear end of the refrigerator main body 61).

  In addition, when a tall hermetic compressor is applied as in the related art, the vibration generated by the hermetic compressor is large, and the vibration transmitted to the refrigerator body is also large. Therefore, by adopting the refrigerator 60B to which the hermetic compressor 100 of the present embodiment is applied, the vibration can be reduced by the above-described structure, so that the vibration transmitted to the refrigerator main body 61 can be suppressed. Further, by applying the small hermetic compressor 100, it is also possible to increase the internal capacity of the storage chamber 62.

  FIG. 5 is a graph showing the relationship between the frequency and the sound pressure level during operation of the compressor. By increasing the plate thickness of the frame, it can be confirmed that the vibration of the compression element transmitted to the closed casing 3 via the coil spring 9 can be attenuated over a wide frequency range.

  Therefore, in the present embodiment, in order to realize a compressor with a reduced height (flat), the thickness and thickness of the frame are increased to increase the mass and rigidity, thereby suppressing noise and vibration. If the compressor is simply reduced in size (for example, flattened), the mass of the compressor is reduced and the vibration damping ability is reduced. For this reason, when designing to reduce the volume of the compressor, it is preferable to pay attention to maintaining the mass itself as much as possible. In the present embodiment, the mass is 7.3 kg or more while the height is suppressed to 130 mm or less. Note that the internal volume of the hermetic compressor of the present embodiment (the internal volume of the hermetic container 3) is 1300 mL or less. The thickness of the frame 24 at the thinnest portion is 11 mm or more, preferably 13 mm or more, more preferably 15 mm or more.

3 Closed container 3a Step 9 Coil spring (elastic member)
DESCRIPTION OF SYMBOLS 10 Rubber seat 20 Compression element 21 Cylinder 22 Piston 23 Crankshaft 24 Frame 24a Base 24b Through hole 24c Depression 24d Extension part 25 Radial bearing (bearing)
26 thrust bearing 30 electric element 31 rotor 32 stator 100 hermetic compressor

Claims (3)

In a hermetic compressor including a compression element including a piston and a cylinder serving as a vibration source, an electric element that drives the compression element and includes a stator, a sealed container that houses the compression element and the electric element, and a frame. ,
The cylinder is disposed above the frame, the stator is disposed below the frame,
The frame is supported by the closed container via at least two elastic members provided on each of the compression element side and the opposite side of the compression element side ,
The elastic member is connected to a lower surface of the frame ,
The frame is connected to said elastic member, and a protrusion that protrudes downward, the hermetic compressor according to claim Rukoto to have a, a protrusion upper projecting toward the upper case of the closed container . The hermetic compressor according to claim 1 , wherein a height position of a center of gravity of the hermetic compressor is within a range of height positions of the frame . An apparatus equipped with the hermetic compressor according to claim 1 or 2 .

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