Hermetically sealed compressor

Abstract: A hermetically sealed compressor for use in household appliances such as refrigerators comprising an electric element (22) and a compression element (23) being resiliently supported within a hermetic container (21). The crankshaft (51) is secured to a rotor (25) of an electric element and supported by a pair of ball bearings (55,56). The crankshaft is comprised of a concentric principal part (52), a concentric secondary part (53) and an eccentric axial part (54) positioned between the principal part and the secondary part. The eccentric axial part is connected to one end of a connecting rod (30). In one embodiment, the eccentric axial part overlays all of the principal part and secondary part when seen in plan or projection view from the axial direction of the crankshaft. One of a pair of ball bearings is installed in each of the concentric principal part and secondary part respectively so as to support the load caused by the reaction of the compression load equally on each side of the axis along which the force of that load is exerted.

Description: BACKGROUND OF THE INVENTION (Field of the Invention) This invention relates generally to hermetically sealed compressors, and more particularly to small hermetically sealed refrigeration compressors, used in household appliances such as refrigerators and food freezers. (Description of Prior Art) Because of high energy costs and various governmental requirements, household appliances are being extensively redesigned to increase their energy efficiency. In the case of refrigerators, substantial improvements have been made by various improvements of the refrigeration system itself, including improvements in the size of evaporators and condensers. One of the objectives that has received the most attention is to increase the efficiency of refrigeration compressors. Increases in compressor efficiency have come primarily from increases in the electrical efficiency of motors which drive the compressors and from increases in pump volumetric efficiency. Decreasing the bearing friction of a principal rotating part, such as a crankshaft, in such compressors, will also contribute to increasing the efficiency of a refrigeration compressor. A conventional hermetically sealed compressor of the type referred to above for, use in household appliances such as refrigerators, is described here with reference to Fig. 7 (as also disclosed in Japanese Laid-open Patent Applications No. 63-5186). In Fig. 7, electric element 1 and compression element 2 are generally resiliently supported within and in spaced relationship to hermetic container 3. Electric element 1 comprises stator 4, rotor 5, and crankshaft 6. Rotor 5 is pressed in place on crankshaft 6. Ball bearings 7, 8 are securely positioned at both upper and lower ends of bearing hub 9 to support the weight of rotor 5 and crankshaft 6. At its lower end, crankshaft 6 carries an eccentric axial part 10, which is integrally formed in a single molding with crankshaft 6. Eccentric axial element 10 fits within one end of connecting rod 11 and the other end of connecting rod 11 is connected to piston 12 which is slidably positioned within cylinder 13. In the above-described structure, in operation, the compressor is driven by stator 4 and rotor 5 powered by connection with a source of electrical energy (not shown) and piston 12 is reciprocated in cylinder 13 to compress refrigerant gasses. However, this conventional hermetically sealed compressor may have some collateral disadvantages which include: (a) Because of a cantilever structure, that is, both ball bearings 7 and 8 are installed at the same side in regard to the axis of cylinder 13, ball bearings 7 and 8 are heavily loaded in operation. Fig. 8 shows a schematic force diagram of ball bearings 7, 8 as they are loaded in operation. W is a reaction force to the compression action. L is the distance between ball bearing 8 and axis 13A of cylinder 13. K is the distance between ball bearings 7 and 8. J is the distance between ball bearing 7 and axis 13A of cylinder 13. As shown in Fig. 8, ball bearing 7 is pressed by the force of W·L/K which is larger than W in the direction shown by arrow A. Ball bearing 8 is also heavily pressed by the force of W·J/K in the direction shown by arrow B. Accordingly, the above-described structure may cause a reduction in the life span of both ball bearings 7 and 8, and it may be very difficult to assure the reliability of such a structure. (b) In general, it is necessary to pressurize both ball bearings 7 and 8 (i.e. hold them under pressure against the crankshaft) in order to assure the reliability and reduce the noise of a structure as shown in Fig. 7. In this conventional hermetically sealed compressor of Fig. 7, though ball bearing 8 is pressurized by the deadweight of compression element 2, it is necessary to pressurize ball bearing 7 by additional means which increases the number of parts required. (c) In this structure, because of the radial clearance required (particularly as bearings wear), it is necessary to provide a space S in view of assembly clearance dimensions between stator 4 and rotor 5. The space S may makes compressor operation unstable and also cause a reduction in motor efficiency. Prior art document GB-A-846,264 discloses an electric refrigerator motor-compressor unit including a vertical crankshaft having a bottom bearing, wherein lubricant is fed to the walls of said bearing through a lateral passage extending outwardly from a central longitudinal passage of the shaft in communication with a lubricant reservoir, is fed up the bearing walls and is then fed inwardly through a further lateral passage to a further longitudinal passage to other parts of the shaft requiring lubrication. The principal object of the invention is to provide a hermetically sealed compressor with improved life span and reliability by reducing the load on ball bearings in the operation of the compressor. Another object of preferred embodiments of the invention is to stabilize the efficiency of the hermetically sealed compressor by stabilizing the space between rotor and stator. Further objects and advantages reside in the cooperation of parts of the structure which facilitates the operation and the assembly of the hermetically sealed compressor. According to the present invention, there is provided a hermetically sealed compressor comprising: an electric element having a rotor and a crankshaft; a compression element having a connecting rod; and a hermetic container resiliently supporting said electric element and compression element therein; said crankshaft secured to said rotor of the electric element and supported by a pair of bearings, said crankshaft comprising a first part and an eccentric axial part said eccentric axial part being connected to one end of said connecting rod, characterized in that said eccentric axial part is positioned at the upper end of the crankshaft; and in that: said bearings are ball bearings; a first one of said ball bearings is installed in mating contact with said first part of said crankshaft, a second one of said ball bearings is installed in mating contact with said eccentric axial part coaxially with said first one of said ball bearings, a spacer having an eccentric hole is inserted in an inner washer of said second one of said ball bearings, and in that said eccentric axial part of said crankshaft is inserted in said eccentric hole of the spacer. A divisional application is to relate to other types of hermetically seal compressors. The structure, organization and operation of the invention will now be described more specifically in the following detailed description with reference to the accompanying drawings, in which: Fig. 1 is a longitudinal cross sectional view, showing the structure of a hermetically sealed compressor according to the invention of the divisional application referred to above; Fig. 2 is a longitudinal cross sectional view, showing the structure of a preferred hermetically sealed compressor according to the present invention; Fig. 3 is a fragmentary plan view of the hermetically sealed compressor of Fig. 2 taken in the plane A-A of Fig. 2; Fig. 4 is a longitudinal cross sectional view, showing the structure of another preferred hermetically sealed compressor according to the invention of the divisional application referred to above; Fig. 5 is a fragmentary plan view of the hermetically sealed compressor of Fig. 4 taken in plane A-A of Fig. 4; Fig. 6 is a plan view of the crankshaft of the hermetically sealed compressor illustrated in Fig. 4 in a direction downwardly from the top of the compressor, that is, as shown by arrow B in Fig. 4; Fig. 7 is a longitudinal cross sectional view, showing the structure of a conventional hermetically sealed compressor; Fig. 8 is a schematic force diagram of the ball bearing of the conventional hermetically sealed compressor illustrated in Fig. 7, in operation. DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS Referring to the drawings in greater detail, Fig. 1 shows a preferred embodiment of the invention to which the divisional application relates, this being a hermetically sealed compressor which is particularly adaptable for use with refrigeration apparatus wherein a refrigerant is compressed, condensed and evaporated in a repeated cycle. The compressor includes a hermetic container 21 which hermetically seals the interior of the compressor and whose surface is unbroken except for inlet and outlet lines and the electrical connector (not shown in Fig. 1). Within the hermetic container 21 are mounted an electric element 22 and a compression element 23. In general, electric element 22 and compression element 23 are resiliently supported within and in spaced relationship with hermetic container 21. The electric element 22 comprises stator 24, rotor 25, and crankshaft 26. The rotor 25 is mounted concentrically within the stator 24 and secured to crankshaft 26, so that after rotor 25 is pressed in place on crankshaft 26, crankshaft 26 and rotor 25 form a single unitary assembly. The crankshaft 26 comprises a principal concentric part 27, a secondary concentric part 28 and an eccentric axial part 29, all of which (27, 28, 29) are integrally formed as a single molding. The principal part 27 and secondary part 28 are coaxial. The eccentric axial part 29 is positioned between principal part 27 and secondary part 28 and eccentric from both principal part 27 and secondary part 28. The compression element 23 comprises connecting rod 30, piston 31 and cylinder 32. The eccentric axial part 29 fits within one end of connecting rod 30 and the other end of connecting rod 30 is connected to piston 31. Ball bearing 33 is located with electric element 22 on one side of axis 32A of cylinder 32 and pressed in place on principal part 27. A sliding bearing 38 is located on the other side of axis 32A of cylinder 32 (that is the side of axis 32A other than that on which the electric element 22 is located). Secondary part 28 is inserted in sliding bearing 38. An outer washer 33a of ball bearing 33 is inserted in housing 34 and the dead weight of both crankshaft 26 and rotor 25 are supported by contact at face 35 with both housing 34 and outer washer 33a. Housing 34 and cylinder 32 are integrally formed as a single molding. Ball bearing 33 and sliding bearing 38 are provided with a continuing oil supply by an oil pump (not shown in Fig. 1) The reciprocating piston 31 is also lubricated within cylinder 32. Other things are standard and well known in the art and therefore further explanation is omitted. In assembly, first, ball bearing 33 is pressed in place on principal part 27 of crankshaft 26. Then crankshaft 26 is inserted in housing 34. After that, sliding bearing 38 and cylinder 32 are secured by bolt 32B, and later connecting rod 30 which consists of two part is installed by assembly with eccentric axial part 29. In operation, the compressor is driven by a suitable electrical energy source and piston 31 is reciprocated in cylinder 32 to compress refrigerant gasses. In this device because ball bearing 33 and sliding bearing 38 are arranged on opposite sides of axis 32A (that is one is on the same side of axis 32A as the electric element and the other is on the side of axis 32A of cylinder 32 away from the electric element, respectively), the load caused by reaction to the compression load is equally supported by both ball bearing 33 and sliding bearing 38. Consequently, this reduces the loads on ball bearing 33 and sliding bearing 38 in operation and also improves the life span and reliability of both ball bearing 33 and sliding bearing 38. Also because the dead weight of both crankshaft 26 and rotor 25 are supported at outer washer 33a of ball bearing 33, ball bearing 33 is structurally pressurized without additional pressurizing means. Figs 2 and 3 show a preferred embodiment of the present invention, which has significant differences from the embodiment of the divisional application previously described. At its upper end, crankshaft 41 carries an eccentric axial part 42 which is eccentric from crankshaft 41. Both crankshaft 41 and eccentric axial part 42 are integrally formed as a single molding. Eccentric axial part 42 fits within one end of connecting rod 30 and the other end of connecting rod 30 is connected to piston 31. Ball bearing 43 is located on the electric element (22) side of axis 32A of cylinder 32 and pressed in place on crankshaft 41. Another ball bearing 44 is located on the other side (i.e. the side away from electric element 22) of axis 32A of cylinder 32 and installed coaxially with ball bearing 43. A spacer 45, having a hole 46, is pressed in place on inner washer 44a of ball bearing 44. The hole 46 is eccentric from the axis of ball bearing 44 and the eccentric location, or radial offset, of hole 46 corresponds to the radial distance between the axis of crankshaft 41 and the axis of eccentric axial part 42. Eccentric axial part 42 is inserted in hole 46 of spacer 45. In assembly, first, ball bearing 43 is pressed in place on crankshaft 41. Then spacer 45 is pressed in place on inner washer 44a of ball bearing 44. After that, eccentric axial part 42 is inserted in one end of connecting rod 30 and later eccentric axial part 42 is inserted in hole 46 of spacer 45. In this preferred embodiment, as in the embodiment of the divisional application described above, the load caused by the reaction of the compression load are equally supported by both ball bearings 43 and 44. This consequently improves the life span and reliability of both ball bearings 43 and 44. Also, the longer distance between ball bearings 43 and 44, in comparison with the conventional example described above, reduces the required clearance dimension between rotor 25 and stator 24. This in turn leads to stabilization and better motor efficiency. And also, because there is no need of a secondary axial part, as shown in Fig. 1, assembly of the device is facilitated in that processing is easier and it is not necessary to divide connecting rod 30 for assembly. Figs. 4, 5 and 6 a show still another embodiment of the invention to which the divisional application relates, which has significant differences from the devices previously described. In this embodiment, crankshaft 51 comprises principal part 52, secondary part 53 and eccentric axial part 54. Part 54 is positioned between principal part 52 and secondary part 53. All of them (52, 53, 54) are integrally formed as a single molding. Ball bearing 55 is positioned on the electric element (22), side of axis 32A of cylinder 32, and pressed in place on principal part 52. Another ball bearing 56 is located on the other side of axis 32A of cylinder 32 and pressed in place on secondary part 53. Eccentric axial part 54 fits within one end of connecting rod 30 and the other end of connecting rod 30 is connected to piston 31. In this embodiment, eccentric axial part 54 covers or overlays all of principal part 52 and secondary part 53, when seen in projection or plan view. This is best seen in a projection view from the axis direction of crankshaft 51 as indicated in Fig. 6. In assembly, first, piston 31 with connecting rod 30 is inserted in cylinder 32. Then crankshaft 51 is inserted in one end of connecting rod 30. After that, block 60 and cylinder 32 are secured by bolt 32B and later, ball bearings 55 and 56 are pressed in place on both principal part 52 and secondary part 53. As in the other devices discussed above, in this embodiment of the divisional application which is also similar to the embodiment of the divisional application described earlier in certain respects, a load caused by the reaction of the compression load is equally supported by both ball bearings 55 and 56. This consequently improves the life span and reliability of both ball bearings 55 and 56. In comparison with the conventional design described above, the improved bearing life reduces the increase in clearance between rotor 25 and stator 24, which otherwise develops as bearings wear. This leads to stabilization of motor efficiency. Further, because there is no need of a secondary axis, processing is easier and dividing connecting rod 30 for assembly is unnecessary. As can be seen, this invention improves the life span and reliability of a ball bearing by reducing the load on the ball bearing in operation, and also stabilizes the efficiency of the hermetically sealed compressor by stabilizing the space between rotor and stator. In this device also, processing and assembly of the hermetically sealed compressor is facilitated. It should be understood that various other modifications of the present invention will be apparent to and can be readily made by those skilled in the art without departing from the scope of this invention. Accordingly, it is not intended that the scope of the claims appended hereto be limited to the description as set forth herein.

Claims: A hermetically sealed compressor comprising: an electric element (22) having a rotor (25) and a crankshaft (41); a compression element (23) having a connecting rod (30); and a hermetic container (21) resiliently supporting said electric element (22) and compression element (23) therein; said crankshaft (41) secured to said rotor (25) of the electric element (22) and supported by a pair of bearings (43,44), said crankshaft (41) comprising a first part and an eccentric axial part (42), said eccentric axial part (42) being connected to one end of said connecting rod (30), characterized in that said eccentric axial part is positioned at the other end of the crankshaft; and in that: said bearings (43,44) are ball bearings; a first one of said ball bearings (43) is installed in mating contact with said first part of said crankshaft, a second one of said ball bearings (44) is installed in mating contact with said eccentric axial part (42) coaxially with said first one of said ball bearings (43), a spacer (45), having an eccentric hole (46) is inserted in an inner washer (44a) of said second one of said ball bearings (44), and in that said eccentric axial part (42) of said crankshaft (41) is inserted in said eccentric hole (46) of the spacer (45).

Inventors: KAWAI HIDEKI, OSAKA MASAHIKO, WADA SATOSHI, KAWAI, HIDEKI, OSAKA, MASAHIKO, WADA, SATOSHI
Applicants: MATSUSHITA REFRIGERATION, MATSUSHITA REFRIGERATION COMPANY
Application year: 1991
Main classification: F04B39
IPC codes: F04B9, F04B39