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Hermetic compressor

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Title: Hermetic compressor.
Abstract: A hermetic compressor includes a hermetic container; a compression unit arranged in the hermetic container that has a refrigerant compression chamber. A drive unit is configured to provide a refrigerant compression and a charger configured to deliver a refrigerant remaining in the hermetic container outside the refrigerant compression chamber into the refrigerant compression chamber. The charger may include a fan configured to rotate upon receiving a driving force from the drive unit, as well as a channel configured to deliver the refrigerant blown by the fan into the refrigerant compression chamber. ...


- Washington, DC, US
Inventor: Seung Don Seo
USPTO Applicaton #: #20070014678 - Class: 417423130 (USPTO) - 01/18/07 - Class 417 


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Related Patent Categories: Pumps, Motor Driven, Electric Or Magnetic Motor, Rotary Motor And Rotary Nonexpansible Chamber Pump, Having Bearing, With Lubricator
The Patent Description & Claims data below is from USPTO Patent Application 20070014678, Hermetic compressor.



CROSS REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of priority under 35 U.S.C. .sctn. 119 to Korean Patent Application No. 2005-62569, filed Jun. 12, 2005, the entire contents of which is incorporated herein by reference. This application may also be related to commonly owned U.S. Pat. No. 6,893,233, as well as to commonly owned U.S. patent application Ser. No. 11/199,170, filed Aug. 9, 2005, the entire contents of each of which are herein incorporated by reference.

BACKGROUND OF THE INVENTION

[0002] 1. Field of the Invention

[0003] The present invention relates to a compressor, and, more particularly, to a compressor in which a low speed motor is employed to reduce drive noise while preventing degradation in compression capacity.

[0004] 2. Description of the Related Art

[0005] Generally, a refrigeration cycle employed in an air conditioner or refrigerator uses a compressor to suction and compress a low-pressure refrigerant (thereby generating a high pressure refrigerant) and to discharge the compressed high-pressure refrigerant, a condenser to condense the refrigerant discharged from the compressor, an expansion member to expand the condensed refrigerant delivered from the condenser, and an evaporator in which the expanded refrigerant delivered from the expansion member exchanges heat with the atmosphere via evaporation. The compressor, condenser, expansion member, and evaporator are interconnected by use of refrigerant pipes to form a closed circuit.

[0006] In consideration of the capacity of the refrigeration cycle, the motor for use in the compressor of the refrigeration cycle is mainly a two pole motor having a commercial rotational speed of 3000 rpm to 3600 rpm.

[0007] However, the conventional refrigeration cycle compressor has a problem in that the high speed two pole motor generates excessive drive noise due to vibration during high speed rotation thereof.

[0008] Although a low speed four pole motor having a commercial rotational speed of 1500 rpm to 1800 rpm may be substituted for the two pole motor to reduce the drive noise of the compressor, the low speed motor exhibits only low compression capacity due to its low RPM, inhibiting effective implementation of a refrigerant compression operation.

SUMMARY OF THE INVENTION

[0009] Therefore, the present invention has been made in order to solve the above problems, and it is an aspect of the invention to provide a compressor in which a low speed motor is employed to reduce drive noise while preventing degradation in compression capacity.

[0010] Accordingly, one aspect of the present invention provides a hermetic compressor, the hermetic compressor including a hermetic container; a compression unit arranged in the hermetic container and including a refrigerant compression chamber; a drive unit configured to provide a refrigerant compression power, the drive unit including a low speed motor having at least four poles; and a charger configured to deliver a refrigerant remaining in the hermetic container outside the refrigerant compression chamber into the refrigerant compression chamber. The charger may further include a fan configured to rotate upon receiving a driving force from the drive unit, and a channel configured to deliver the refrigerant blown by the fan into the refrigerant compression chamber.

[0011] Yet another non-limiting aspect of the present invention provides hermetic compressor that includes: a hermetic container; means for compressing a refrigerant; means for providing a compression power while minimizing noise; and means for delivering a refrigerant from the hermetic container into the means for compressing.

[0012] A third non-limiting aspect of the present invention relates to a hermetic compressor, the hermetic compressor including: at least one hermetic container; at least one compression unit including a compression chamber; at least one motor configured to provide power; and at least one super-charger. The super-charger may also include: a super-charge fan configured to rotate, and a super-charge channel configured to deliver refrigerant blown by the super-charge fan into the compression chamber.

[0013] Additional aspects and/or advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

[0014] These and other aspects and advantages of the invention will become apparent and more readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings, of which:

[0015] FIG. 1 is an elevational view of a hermetic compressor in section according to an embodiment of the present invention;

[0016] FIG. 2 is an exploded perspective view of a super-charger according to an embodiment of the present invention;

[0017] FIG. 3 is an elevational view of the super-charger in section, showing the operation of the super-charger when a piston performs a suction stroke;

[0018] FIG. 4 is an elevational view of the super-charger in section, showing the operation of the super-charger when a piston performs a compression stroke; and

[0019] FIG. 5 is an elevational view of the super-charger in section taken along line A-A of FIG. 3.

DETAILED DESCRIPTION OF THE EMBODIMENTS

[0020] Reference will now be made in detail to the non-limiting embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to like elements throughout.

[0021] In operation, as refrigerant circulates through refrigeration cycle, it discharges heat to the atmosphere while being condensed in a condenser and also absorbs heat from the atmosphere while being evaporated in an evaporator. To overcome this, an evaporator enables the implementation of a cooling operation.

[0022] In more detail, the compressor may include a hermetic container, a compression unit to compress a refrigerant, and a motor to provide refrigerant compression power. The compression unit and the motor may be arranged in the hermetic container at desired locations. The hermetic container may also be provided with a suction pipe so that the refrigerant, delivered from the evaporator, is introduced into the hermetic container, and a discharge pipe so that the refrigerant is discharged from the hermetic container into a condenser after being compressed in the compression unit.

[0023] With the above-described configuration, the refrigerant, which has been delivered from the evaporator into the hermetic container of the compressor by way of the suction pipe, is compressed in the compression unit in accordance with driving of the motor. Subsequently, the compressed refrigerant is discharged from the hermetic container into the condenser by the discharge pipe.

[0024] Referring to FIG. 1, the compressor may include a hermetic container 1, which may be divided into upper and lower containers 1a and 1b coupled to each other; a compression unit 10 to compress a refrigerant; and a drive unit 20 to provide a refrigerant compression power, the compression unit 10 and the drive unit 20 being arranged in the hermetic container 1 at desired locations. The hermetic container 1 may be provided at a location with a suction pipe 2 to introduce a refrigerant, which may be supplied from an evaporator of a refrigeration cycle, into the hermetic container 1 and at another location with a discharge pipe 3 to discharge the refrigerant from the hermetic container 1 to a condenser of the refrigeration cycle after being compressed in the compression unit 10.

[0025] The compression unit 10 may include a cylinder block 11, a piston 12, a cylinder head 13, and a valve device 14. The cylinder block 11 may be located at a lateral location of a frame 30 and may internally define a refrigerant compression chamber 11a. The piston 12 may be adapted to linearly reciprocate in the compression chamber 11a to compress a refrigerant. The cylinder head 13 may be coupled to the cylinder block 11 to hermetically seal the compression chamber 11a. The cylinder head 13 may internally define a refrigerant discharge chamber 13a and a refrigerant suction chamber 13b. The valve device 14 may be interposed between the cylinder block 11 and the cylinder head 13 to control the flow of a refrigerant, so that the refrigerant is introduced from the refrigerant suction chamber 13b into the compression chamber 11a or is discharged from the compression chamber 11a into the refrigerant discharge chamber 13a.

[0026] The drive unit 20 may provide a driving force to reciprocate the piston 20 in the compression chamber 11a. The drive unit 20 may include a motor having a stator 21 fixed in the hermetic container 1, a rotor 22 spaced apart from the stator 21 to electromagnetically interact with the stator 21, and a rotating shaft 23 press fitted in the center of the rotor 22 to rotate along with the rotor 22. According to a non-limiting aspect of the present invention, the motor may include a four pole motor having a commercial rotational speed of 1500 rpm to 1800 rpm at a frequency of 50 Hz to 60 Hz. Accordingly, the stator 21 may be a four pole stator.

[0027] When the drive unit 20 includes the four pole motor, the rotational speed of the rotating shaft 23 may be half of the rotational speed of a two pole motor that can alternatively be used in a refrigeration cycle compressor. Accordingly, the drive unit 20 may be able to greatly reduce vibration generated during rotation thereof, so that substantially no drive noise of the compressor is detected outside of hermetic container 1.

[0028] The rotating shaft 23 may include a main shaft section 23a, an eccentric shaft section 23b, and a weight balance section 23c between the main shaft section 23a and the eccentric shaft section 23b. The main shaft section 23a may be rotatably supported in a center hollow portion 31 of the frame 30, and a lower end portion of the main shaft section 23a may be press fitted in the rotor 22. The eccentric shaft section 23b may be located above the main shaft section 23a to be aligned eccentric to the main shaft section 23a. The weight balance section 23c may have a plate shape, and may compensate for an unbalanced rotating motion of the rotating shaft 23 due to the eccentric shaft section 23b. A connecting rod 25 may be interposed between the eccentric shaft section 23b and the piston 12. Specifically, one end of the connecting rod 25 may be coupled to the eccentric shaft section 23b in a rotatable manner, and the other end of the connecting rod 25 may be coupled to the piston 12 in a rotatable and linearly movable manner, to convert an eccentric rotating motion of the eccentric shaft section 23b into a linear motion of the piston 12.

[0029] In FIG. 1, reference numeral 41 denotes a thrust ball bearing optionally interposed between the rotating shaft 23 and the frame 30, more particularly, optionally interposed between the weight balance section 23c and an upper end of the hollow portion 31. The thrust ball bearing may rotatably support the rotating shaft 23. Reference numerals 42 and 43 denote an oil pickup member and an oil pickup blade, respectively, which may be used to draw oil, from an oil sump 1c defined in the bottom of the hermetic container 1 into an oil channel formed in the rotating shaft 23 when the rotating shaft 23 rotates. The drawn oil may be delivered to several frictional regions of the compressor for lubrication.

[0030] A suction muffler 44 may be interposed between the refrigerant suction chamber 13band the suction pipe 2 to reduce flow noise of the refrigerant generated when the refrigerant may be introduced into the compression chamber 11a. Also, a discharge muffler 45 (see, e.g., FIG. 2) may be interposed between the refrigerant discharge chamber 13a and the discharge pipe 3. The discharge muffler 45 may internally define a resonance space for reducing flow noise of the refrigerant generated when the refrigerant is discharged to the outside of the hermetic container 1. The discharge muffler 45 may be integrally formed with the cylinder block 11 at one side of the compression chamber 11a.

[0031] With the above-described configuration, if electric current is applied, the rotating shaft 23 rotates along with the rotor 22 in accordance with electric interaction between the stator 21 and the rotor 22, so that the piston 12, which may be connected to the eccentric shaft section 23b via the connecting rod 25, linearly reciprocates in the compression chamber 11a. With such a linear reciprocating motion of the piston 12, a refrigerant is introduced into the hermetic container 1 by the suction pipe 2. The introduced refrigerant may be delivered into the refrigerant suction chamber 13b of the cylinder head 13 while being reduced in noise to some extent in accordance with operation of the suction muffler 44. After that, the refrigerant may be delivered into the compression chamber 11a to be compressed therein. Then, the compressed refrigerant may be discharged into the refrigerant discharge chamber 13a of the cylinder head 13. Subsequently, the refrigerant may be discharged to the outside of the hermetic container 1 by the discharge muffler 45 and the discharge pipe 3. Through the repetitive suction and discharge of the refrigerant, the compressor can carry out a refrigerant cooling operation.

[0032] The hermetic compressor according to the present invention may further include a super-charger 60 to increase the amount of refrigerant to be introduced into the compression chamber 11a. The super-charger 60 may compensate for a reduction in the compression capacity of the compressor due to a low RPM of the rotating shaft 23. With the use of the super-charger 60, the compressor according to the present invention is able to achieve a desired refrigerant compression capacity required in a refrigeration cycle, despite the fact that the drive unit 20 may use a low speed four pole motor.

[0033] Part of the refrigerant, which has been introduced into the hermetic container 1 via the suction pipe 2, may remain in the hermetic container 1, rather than being introduced into the refrigerant suction chamber 13b of the cylinder head 13 by the suction muffler 44. The super-charger 60 may compress the refrigerant remaining in the hermetic container and may deliver the compressed refrigerant into the compression chamber 11a, thereby allowing an increased amount of refrigerant to be introduced into the compression chamber 11a. The super-charger 60 may be driven upon receiving power from the drive unit 20 without requiring a separate drive device, so that it compresses and delivers the refrigerant remaining in the hermetic container into the compression chamber 11a.

[0034] Now, the configuration of the super-charger 60 will be explained in detail with reference to FIGS. 2-5. FIG. 2 is an exploded perspective view showing the configuration of the super-charger according to a non-limiting aspect of the present invention. FIGS. 3 and 4 are sectional views showing a non-limiting example of an operation of the super-charger when the piston performs a suction stroke and a compression stroke, respectively. FIG. 5 is a sectional view taken along line A-A of FIG. 3.

[0035] As shown in FIGS. 2-5, the super-charger 60 may include a super-charge fan 70 fitted around the rotating shaft 23 to rotate along with the rotating shaft 23, a super-charge channel 80 to deliver the refrigerant, blown by the super-charge fan 70, into the compression chamber 11a, and a guiding member 90 to guide the refrigerant, blown by the super-charge fan 70, to an entrance of the super-charge channel 80.

[0036] The super-charge fan 70 may include a centrifugal fan. Thus, the refrigerant remaining in the hermetic container 1 may be introduced into a central portion of the super-charge fan 70, and may be discharged to the outside of the fan 70 in a radial direction.

[0037] The centrifugal super-charge fan 70 may include an upper ring-shaped shroud 71 having a center suction opening 71a, a lower hub disk 72 spaced apart downward from the shroud 71 to define discharge slots 72a therebetween, and a plurality of blades 73 circumferentially arranged between the shroud 71 and the hub 72 along the outer periphery of the hub 72.

[0038] The super-charge fan 70 may be fitted around the eccentric shaft section 23b between the weight balance section 23c and the connecting rod 25 so that a center axis thereof coincides with a center axis of the main shaft section 23a of the rotating shaft 23. The super-charge fan 70 may rotate at the same speed as the rotating shaft 23 so that it rotates one turn whenever the rotating shaft 23 rotates one turn.

[0039] The super-charge fan 70 may be fixed to and supported by the rotating shaft 23 as the hub 72 may be fastened to the weight balance section 23c by use of a bolt 100. The super-charge fan 70 may be downwardly fitted onto the eccentric shaft section 23b so that it may be located around a lower portion of the eccentric shaft section 23b. For the penetration of the eccentric shaft section 23b, the hub 72 may be perforated with a through-hole 72b.

[0040] The super-charge channel 80, which may be provided to deliver the refrigerant blown by the super-charge fan 70 into the compression chamber 11a, may include a super-charge chamber 81 configured to communicate with the interior space of the hermetic container 1 and a communication channel 82 to connect the super-charge chamber 81 to the compression chamber 11a.

[0041] The super-charge chamber 81 may be defined in a super-charge casing 81a, which may be integrally formed with the cylinder block 11 at an opposite side of the discharge muffler 45. The communication channel 82 may be perforated through the cylinder block 11 between the super-charge chamber 81 and the compression chamber 11a. An entrance of the super-charge chamber 81 may be the entrance of the super-charge channel 80, and an exit of the communication channel 82 may be an exit of the super-charge channel 80.

[0042] The guiding member 90, which may be provided to guide the refrigerant, blown by the super-charge fan 70, into the entrance of the super-charge channel 80, may include a cylindrical ring-shaped body 91 fitted around the super-charge fan 70 so that a lower end of the body 91 may be closed by an upper surface of the frame 30 along an outer periphery of the hollow portion 31. A hopper 92 may be integrally formed at a location of the body 91 to connect the super-charge chamber 81 to the interior space of the body 91. The hopper 92 may have a funnel shape so that an inner cross sectional area may be reduced from the body 91 toward the super-charge chamber 81. An insert 93 may be formed at a distal end of the hopper 92 to be inserted into the entrance of the super-charge channel 80.

[0043] The reason why the hopper 92 may be formed so that the inner cross sectional area may be reduced toward the entrance of the super-charge chamber 81 is to utilize the Bernoulli's theorem such that when a fluid passes through a narrowing passage, the flow rate of the fluid increases. When the refrigerant is introduced into the super-charge chamber 81 in accordance with a blowing operation of the super-charge fan 70, the hopper 92 may increase the flow rate of the refrigerant, thereby facilitating a smooth supply of the refrigerant.

[0044] The body 91 may be provided with a plurality of support pieces 91a. The support pieces 91 may protrude inward from the lower end of the body 91, and may be used to fasten the body 91 to the upper surface of the frame 30 by use of bolts 100. The insert 93 may be provided at a distal end thereof with a hook 93a. The hook 93a may be caught by and supported in the entrance of the super-charge chamber 81 when the insert 93 is inserted into the entrance. With the use of the bolts 100 and the hook 93a, the guiding member 90 can be kept in a firmly fixed state even when vibrations are generated during the operation of the compressor. Also, to keep the super-charge chamber 81 in an air-tight state, an O-ring 94 may be fitted between the hopper 92 and the insert 93 to hermetically seal the entrance of the super-charge chamber 81.

[0045] An opening/closing valve 83 may be provided between the super-charge chamber 81 and the communication channel 82. The opening/closing valve 83 may intercept communication between the super-charge chamber 81 and the compression chamber 11a when the piston 12 performs a compression stroke, and may open communication between the super-charge chamber 81 and the compression chamber 11a when the piston 12 performs a suction stroke.

[0046] Specifically, the opening/closing valve 83 may be used to control the flow of the refrigerant so that the refrigerant is delivered from the super-charge channel 80 into the compression chamber 11a only when the piston 12 performs a suction stroke. If the opening/closing valve 83 is opened when the piston 12 performs a compression stroke, the refrigerant enters the compression chamber 11, hindering a refrigerant compressing operation of the piston 12. To prevent the unintentional opening of the opening/closing valve 83, preferably, a blowing force of the refrigerant delivered into the compression chamber 11a via the super-charge channel 80 may be smaller than a compression force of the refrigerant in the compression chamber 11a.

[0047] In the hermetic compressor of the present invention having the super-charger 60 configured as stated above, before the refrigerant is compressed in the compression chamber 11a in accordance with rotation of the rotating shaft 23, the super-charger 60 may deliver the refrigerant remaining in the hermetic container 1 into the compression chamber 11a, resulting in an increase in the amount of refrigerant to be introduced into the compression chamber 11a. As a result, despite the fact that the drive unit 20 may include the low speed four pole motor (which causes the rotating shaft 23 to exhibit low speed rotation), the hermetic compressor of the present invention has no degradation in compression capacity.

[0048] Hereinafter, the operation and effects of the hermetic compressor according to additional non-limiting aspects of the present invention will be explained. If electric current is applied, the rotating shaft 23 may rotate along with the rotor 22 in accordance with electromagnetic interaction between the stator 21 and the rotor 22, so that the piston 12, which may be connected to the eccentric shaft section 23b via the connecting rod 25, linearly reciprocates in the compression chamber 11a. With such a linear reciprocating motion of the piston 12, a refrigerant may be introduced into the hermetic container 1 by way of the suction pipe 2. The introduced refrigerant may be delivered into the refrigerant suction chamber 13b of the cylinder head 13 while being reduced in noise to some extent in accordance with operation of the suction muffler 44. After that, the refrigerant may be delivered into the compression chamber 11a to be compressed therein. Then, the compressed refrigerant may be discharged into the refrigerant discharge chamber 13a of the cylinder head 13. Subsequently, the refrigerant is discharged to the outside of the hermetic container 1 via the discharge pipe 3. Through the repetitive suction and discharge of the refrigerant, the compressor carries out a refrigerant cooling operation.

[0049] In the hermetic compressor according to the present invention, since the four pole motor may be used as the drive unit 20, RPM of the rotating shaft 23 may be approximately half that of a conventional two pole motor. Accordingly, the rotating shaft 23 exhibits a greatly reduced vibration during rotation thereof, so that drive noise of the compressor may be too small to be recognized outside the hermetic container 1.

[0050] Also, prior to a refrigerant compression operation, the super-charger 60 may deliver the refrigerant remaining in the hermetic container 1 into the compression chamber 11a to allow an increased amount of refrigerant to be introduced into the compression chamber 11a. The compressor of the present invention can prevent degradation in compression capacity thereof even for a low speed rotation of the rotating shaft 23 in accordance with driving of the four pole low speed motor serving as the drive unit 20.

[0051] Specifically, as the rotating shaft 23 rotates to lead a refrigerant compression operation, the super-charge fan 70, which may be fitted around the rotating shaft 23 so that the center axis of the main shaft section 23a of the rotating shaft 23 coincides with the center axis of the super-charge fan 70, may rotate at the same speed as the rotating shaft 23. In accordance with rotation of the super-charge fan 70, the refrigerant, remaining in the hermetic container 1 at the outside of the compression chamber 11a, may be introduced into the suction opening 71a formed at an upper location of the super-charge fan 70. The introduced refrigerant may be discharged in a radial direction from the super-charge fan 70 via the discharge slots 72a. The discharged refrigerant may be guided into the body 91 of the guiding member 90. In this case, the refrigerant may be increased in flow rate while passing through the hopper 92 of the guiding member 90. Thereby, the refrigerant may be introduced into the super-charge chamber 81 and the communication channel 82 in this sequence with an increased flow rate.

[0052] After being blown into the communication channel 82, the refrigerant may be supplied into the compression chamber 11a via the opening/closing valve 83 during a suction stroke of the piston 12 along with the refrigerant, which may be delivered from the refrigerant suction chamber 13b of the cylinder head 13. Thereby, an increased amount of refrigerant may be introduced into the compression chamber 11a.

[0053] Although the four pole motor may be used as the drive unit 20 in the above-described embodiment, other various low speed motors, such as a six pole motor, may be substituted for the four pole motor. Also, if the diameter or stroke of the piston 12 is increased in addition to using the super-charger 60, the compressor of the present invention can more effectively compensate for a reduction in refrigerant compression capacity of the compressor due to the low speed motor.

[0054] As apparent from the above description, the present invention provides a compressor in which a low speed motor having at least four poles may be used as a drive unit, thereby achieving a great reduction in drive noise and enabling quiet operation. Also, according to the present invention, through the use of a super-charger, it may be possible to prevent degradation in compression capacity even with the low speed rotation of a rotating shaft.

[0055] Although embodiments of the present invention have been shown and described, it would be appreciated by those skilled in the art that changes may be made in this embodiment without departing from the principles and spirit of the invention, the scope of which is defined in the claims and their equivalents.

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stats Patent Info
Application #
US 20070014678 A1
Publish Date
01/18/2007
Document #
11453856
File Date
06/16/2006
USPTO Class
417423130
Other USPTO Classes
International Class
04B35/04
Drawings
6



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