JPH0684751B2 - Refrigeration compressor - Google Patents

Description

The present invention relates to a refrigerating compressor used for compressing a refrigerant.

U.S. Pat. No. 3,526,942 discloses a technique for facilitating the assembling of a refrigeration compressor and firmly supporting a motor means and a compressor assembly (compression mechanism) in the compressor.

This US patent is the casing of a refrigeration compressor.
Is divided into upper and lower parts, and an annular stator of the motor means and an annular frame located below the annular stator are press-fitted to the outer shell portion on the upper side. The annular frame has a bottom wall and a peripheral wall,
A central cylindrical bearing portion that supports a drive shaft that is rotationally driven by the motor means rotor disposed in the central opening of the stator. The compressor assembly is mounted on the lower surface of the bottom wall of the annular frame by bolts, is installed in the lower outer shell portion so as to be immersed in the oil sump in the outer shell portion, and is driven by the drive shaft. It is supposed to receive. The drive shaft is formed with an oil passage for guiding lubricating oil from the oil reservoir to the bearing portion.

In this conventional example, a muffler chamber for the discharge gas compressed and discharged by the compressor assembly is provided inside the compressor assembly or its housing. The muffling chamber communicates with the upper space through the opening provided in the bottom wall of the annular frame, and the discharge gas discharge pipe is attached to the top wall of the outer shell.

The refrigeration compressor disclosed in U.S. Pat.No. 3,526,942 described above has a structure in which the motor stator and the annular frame are press-fitted to the outer shell, so that the number of fasteners such as bolts is small and the assembling work is easy. However, the members can be firmly supported by coping with vibrations, but they have the following problems.

That is, as described above, in the structure in which the muffling chamber is provided in the housing of the compressor assembly, there are restrictions on the members of the compression mechanism,
The degree of freedom in designing the muffling room for enhancing the noise damping effect is greatly limited. Further, the discharge gas flowing from the opening of the bottom wall of the annular frame to the discharge pipe of the outer shell top wall flows upward through the motor means between the discharge gas and the discharge gas heated to a high temperature due to the compression. Passing through the means increases the temperature of the motor means and shortens its life.

The present invention is intended to provide a novel refrigerating compressor that solves this problem while ensuring the ease of manufacturing and assembling the compressor.

A refrigerating compressor according to the present invention is a motor unit including an outer shell, a compressor assembly installed in the outer shell, a stator and a rotor, the outer shell supporting the stator. Motor means installed in the outer shell and connected to the compressor assembly to drive the compressor assembly by a rotor; and an oil sump provided in the outer shell to the compressor assembly. A lubricating oil supply means for guiding lubricating oil and a discharge muffler for silencing the discharge gas discharged from the compressor assembly, the one end surface of the compressor assembly being opposite to the motor means. The first plate members arranged adjacent to each other, the first plate member having an annular convex peripheral edge along the axial direction of the outer shell at the outer peripheral end, and fixed to one end of the outer shell. Second forming the outer end wall of the outer shell Of the first plate member, which has an annular convex peripheral edge at the outer peripheral end, the annular convex peripheral edge protruding toward the first plate member and fixed by being superimposed on the convex peripheral edge of the first plate member together with the first plate member. A second plate member forming a sound deadening cavity for receiving a discharge gas from the compressor assembly, the second plate member being arranged such that the convex edge thereof is located on an extension line of a peripheral wall of the outer shell. On the other hand, the convex peripheral edge of the first plate member is overlapped with the inner surface of the outer shell and the inner peripheral surface of the convex peripheral edge of the second plate member so as to overlap each other, and the convex peripheral edges of the first and second plate members are And a discharge muffler formed by welding and fixing the outer shell together from the convex peripheral edge of the second plate member and the outer surface side of the outer shell, wherein the discharge gas outlet of the compressor assembly is the discharge gas outlet of the compressor assembly. Open at one end When the first plate member is provided, the opening provided in the first plate member directly overlaps the discharge gas outlet with respect to the one end surface of the compressor assembly, and from the discharge gas outlet into the silencing cavity. It is configured to be engaged so that the flow of the discharge gas is performed through the opening of the first plate member.

As described above, the first plate member and the second plate member forming the outer end wall of the outer shell, which are arranged adjacent to each other on one end surface of the compressor assembly, are overlapped with each other at the annular convex rims of the outer peripheral ends, and The discharge muffler, which is integrally welded and fixed together with the shell to form the sound deadening cavity, is arranged adjacent to the compressor assembly at the position of the one end face of the assembly, and at the same time, outside the outer shell. The end wall is provided by the second plate member and is disposed at one end position of the outer shell, that is, one end position of the entire compressor.

Further, according to the present invention, the discharge gas outlet of the compressor assembly is provided by opening at the one end face of the compressor assembly, while the first plate member has an opening provided in the plate member directly to the discharge gas outlet. Since the compressor assembly is engaged with the one end surface of the compressor assembly so that the discharge gas is directly discharged from the compressor assembly into the silencing cavity of the discharge muffler,
The discharge muffler is arranged at one end position of the entire compressor so that the discharge gas can be discharged directly to the outside. Therefore, while the discharge gas passage structure is simplified, the high temperature discharge gas of the compressor is In addition to preventing the life of the motor means from decreasing by not passing through the means, the suction gas flows in the outer shell while coming into contact with the motor means, thereby actively cooling the motor means to improve its life. It is possible to improve it all the time.

Further, the discharge muffler, which is arranged at one end position of the outer shell or the entire compressor separately from the compressor assembly, does not hinder the freedom of design by the compressor assembly, and the cross section of the outer shell is The size and shape can be freely set within the range of the area, and a sound deadening member such as a baffle plate can be arranged inside as needed to enhance the sound deadening effect.

Further, according to the present invention, an annular convex peripheral edge along the axial direction of the outer shell is provided on the outer peripheral end of the first plate member adjacent to one end surface of the compressor assembly and engaged with the end surface, and an outer end wall of the outer shell. The outer peripheral edge of the second plate member to be formed is provided with annular convex rims facing the first plate member respectively, and these convex rims are superposed on each other and fixed to each other so as to fix the inside of the outer shell by both plate members. The muffler cavity of the discharge muffler, which is airtightly separated from the other part, is formed by partitioning. The convex peripheral edge of the second plate member is located on the extension line of the outer shell, and then the first plate member The convex rims are overlapped on the inner surface of the outer shell and the inner surface of the convex rim of the second plate member, and the convex rims of both plate members and the outer shell are arranged so that the convex rims of the second plate member and the outer surface of the outer shell. Since it is structured to be welded and fixed together from the side, At the shell end, the first plate member is first engaged with the one end surface of the compressor assembly to be assembled, and then the convex peripheral edge of the second plate member is externally inserted into the convex peripheral edge of the plate member while the first plate member is inserted into the outer peripheral end of the outer shell end. After assembling the second plate member, it is possible to complete the assembly of the discharge muffler and the compressor by performing a single welding from the outside. That is, the convex edge of the first plate member, which is overlapped with the inner surface of the outer shell and the inner surface of the convex edge of the second plate member, is overlapped with the outer edge portion of the outer plate and the convex edge of the second plate member which are welded to each other. A backing metal between the peripheral edge, that is, a backing that provides sufficient penetration of the base metal to be welded and prevents foreign matter or contaminants such as welding sludge from entering the outer shell and muffler silencing cavity, At the same time, the first plate member is fixed to the second plate member and the outer shell by being welded together with the base metal to be welded. Assembling the discharge muffler, fixing the second plate member to the outer shell end and providing the outer end wall of the outer shell to complete the assembly of the compressor, once from the outside without any trouble. It can be done in the welding process. Further, the convex edge of the first plate member is arranged so as to function as a backing metal for the outer shell to be welded to each other and the convex edge of the second plate member as described above, so that the welding strength is secured. In addition, it is not necessary to provide an overlapping portion such as a fitting portion or a radially outward flange portion for preventing foreign matter from entering the outer shell between the outer shell and the convex edge of the second plate member. The shapes of the outer shell and the second plate member are simplified to that extent, which facilitates manufacturing. Therefore, according to the present invention, the ease of manufacturing and assembling the compressor is ensured.

Further, the structure in which the convex peripheral edge of the first plate member is laid over the inner surface of the outer shell and the inner peripheral surface of the convex edge of the second plate member and overlapped and welded to the outer shell and the convex peripheral edge of the second plate member, is provided. The airtightness between the muffling cavity and the other parts of the outer shell is greatly enhanced, and the problem that the discharge gas in the high-pressure discharge muffler leaks to the other parts of the low-pressure outer shell to cause a pressure drop of the discharge gas is completely eliminated. As described above, even if the suction gas flows in the outer shell while being in contact with the motor unit to cool the motor unit, a part of the discharge gas enters the other part of the outer shell and is mixed with the suction gas. No trouble will occur.

Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

Referring now to the drawings, FIG. 1-15 illustrates a hermetic electric compressor in accordance with the present invention, generally designated by the reference numeral 10.

The electric compressor 10 includes an outer shell 12 that is hermetically sealed and that is formed in a divided manner. Inside the outer shell 12, a motor stator 16 is provided.
And a compressor assembly 14 that is operatively connected to and driven by an electric motor that includes a motor rotor 18.

The outer shell 12 formed by being divided into a plurality of portions includes upper and lower vertically elongated and substantially circular portions (cylindrical portions) 20 and 22, and each of these cylindrical outer shell portions 20 and 22 includes The flange portions 24, 26 projecting outward in the radial direction are provided, and the flange portions 24, 26 are formed so that they can abut against each other and be fixed. A bottom portion 28 is fixed to the lower end of the lower cylindrical outer shell portion 22.
28, a plurality of installation legs 30 which are arranged intermittently when viewed in the circumferential direction are integrally formed so as to project outward in the radial direction.

Discharge muffler 32 is attached to the upper end of upper cylindrical shell portion 20 and forms a cover for the top end of shell 12. The discharge muffler 32 includes an annular member 34 having inner and outer convex rims 36 and 38, and the convex rims 36 and 38 are the inner and outer convex rims 40 and 42 of the lower material 44 of the discharge muffler 32. They are superposed on each other so that an annular sound deadening cavity 46 is formed between both the members 34, 44 described above. An arch-shaped baffle (baffle) member 48 having a substantially inverted U-shaped cross section has a sound deadening cavity.
Directly to a pair of discharge gas outlets 50 and 52, which are opened in the upper surface of the compressor housing 56 at a distance from each other, as shown in FIGS. It is arranged so as to be overlapped with an opening in the overlapping openings of the lower members 44, and is fixed by a plurality of screw fasteners (bolts) 54.

The above-mentioned two members forming the discharge muffler 32 as shown in FIG.
The convex peripheral edge 36 provided on the outer peripheral end of the muffler member 34 on the upper side of 34, 44 is formed to have the same diameter as the peripheral wall of the outer shell 12, and is located on an extension line of the peripheral wall. On the other hand, the convex peripheral edge 42 provided on the outer peripheral end of the lower muffler member 44 is formed to have a size overlapping the inner surface of the outer shell 12 and the inner surface of the convex peripheral edge 36 of the upper muffler member 32. Has been done. As will be described later, the convex peripheral edges 36 of the upper and lower muffler members 34, 44,
42 and the outer shell 12 are simultaneously welded from the outer side of the outer shell 12 and fixed to each other as illustrated.

Threaded fasteners 54, as clearly shown in FIG. 1, are also utilized to secure the lower members 44 to the compressor 14. The compressor 14 includes a main body (compressor housing) 56 having upper and lower substantially circular flange portions 58 and 60, which are spaced apart from each other, at one end side thereof, and the both flange portions 58 and 60 are , A pair of substantially parallel mirror-symmetrical side walls 62, 64 and a cylinder wall 66 extending between them in a direction substantially orthogonal to the side walls 62, 64. Are linked to.

As clearly shown in FIG. 4, the cylinder wall 66 includes arcuate surfaces 68 and 70 at both ends thereof.
Is a crankcase that is in close contact with the inner peripheral surface of the upper cylindrical outer shell portion 20 of the outer shell 12 and cooperates with the lower flange portion 60 and the lower members 44 of the discharge muffler 32 to substantially close the crankcase. Its shape is set to form. A cylinder hole 72 is provided through the cylinder wall 66, and the cylinder hole 72 concentrically faces the large diameter hole 74 defined by the side walls 62, 64 and the upper and lower flange portions 58, 60. It is located.

The lower flange portion 60 of the main body 56 has a frusto-conical suspension portion 76 having an opening 78 formed therein.
Is intended to receive an elongated stepped bearing 80 which rotatably supports a crankshaft 82. As shown in FIG. 1, the bearing 80 includes an axial thrust receiving shoulder 84 that is abuttable against an annular shoulder 86 provided on the crankshaft 82. A relatively large opening 88 is provided through the upper flange portion 58.
88 is concentrically arranged with the above-mentioned opening 78, and rotatably accommodates the counterweight 90 which is press-fitted to the extension of the crankshaft 82.

A piston 94 is disposed in the cylinder hole 72 so as to be capable of reciprocating, and as shown clearly in FIG.
An irregularly shaped connecting portion for drivingly connecting the piston 94 to the crankshaft 82 is integrally formed, and the connecting portions are arranged in parallel at a distance from each other. It includes a pair of elongated sidewalls 96 and 98. The outer surfaces of the side wall portions 96 and 98 are formed by the large-diameter holes 74 in the compressor housing.
Formed on the cylindrical surface that closely contacts the side wall of the piston and thus the piston
It is supposed that 94 is supported so as to be able to reciprocate sideways. A pair of curved arms 1 between the above-mentioned side wall parts 96, 98
00 and 102 are extended rearward and upward and downward, respectively, and the outer surfaces of the curved arms 100 and 102 are also formed in a cylindrical surface so as to be in close contact with the side wall of the large diameter hole 74, and reciprocate the piston. It serves for support and guidance of 94. An arch-shaped strip 104 is extended between the side walls 96 and 98 in the middle of the curved arms 100 and 102.
04 cooperates with the side wall portions 96 and 98 to form a relatively large-diameter journal hole 106 for drivingly connecting the piston 94 to the crankshaft 92. The strip 104 can be formed to be narrower towards the non-load side of the connection so that the weight of the piston 14 can be reduced without sacrificing reliability. Also, because the lateral pressure applied to the piston 94 in the vertical direction is relatively small,
The cross-sectional area of the curved arms 100, 102 may be substantially smaller than the cross-sectional area of the sidewall portions 96, 98.

A valve plate assembly 108 and a head 110 are provided in such a manner that they overlap the radial outer end of the cylinder bore 72.
The outer surface 112 of the head 110, as clearly shown in FIG.
12 has an arcuate shape complementary to the shape of the upper cylindrical shell portion 20 at 12, the outer surface 112 shape of which the head 110 is tightly anchored by the compressor housing and without any further coupling. It is set to be held in position. The valve plate assembly 108 also extends chordally between the sidewalls of the outer shell portion 20, as shown, and cooperates with the head 110 to prevent fluid leakage between the crankcase and the lower portion of the outer shell 12. To prevent. Head
A suction chamber 114 is included in 110, and the suction chamber 114 communicates with a motor chamber (installation space of an electric motor) through an opening at a lower end thereof, and supplies suction gas to the cylinder hole 72 from there. The head 110 also includes a discharge chamber 116 which receives the discharge gas from the cylinder bore 72 and directs it to the discharge muffler 32 via the discharge gas outlets 50 and 52 described above. The valve plate is, of course, equipped with suitable ports and valves to control the entry and exit of fluids into and from the cylinder bores.

The stator 16 of the electric motor described above is designed to be press-fitted or heat-shrink-fitted into the cylindrical outer shell portion 22 on the lower side of the outer shell 12 so as to be supported only by the outer shell portion 22. Therefore, as clearly shown in FIG. 2, it has a substantially rectangular cross-sectional shape in which four corners are cut out in an arc shape so as to tightly engage with the side wall of the outer shell portion 22. It is said that.
In order to prevent excessive stress from being applied to the outer shell portion 22 and distortion of the shape of the portion 22, the periphery of the motor stator 16 is positioned at the position where the above-mentioned cutout portion and the flat side wall surface portion intersect. The cutout groove 120 for escape is provided. Adjacent corners 118
The space 122 to be formed between the motor stator 16 and the outer shell portion 22 is circulated so that the suction gas passing through the suction port 124 and entering the cylindrical portion 16 is cooled to cool the electric motor. I will let you.

From the above, the electric compressor 10 has an outer shell portion (outer shell) on the upper side.
A compressor assembly 14 directly supported and fixed to the upper cylindrical portion 20 of the outer shell 12) and a lower outer shell portion (lower cylindrical portion of the outer shell 12) 22. And a motor stator 16 which is directly supported and fixed to the portion 22 so that these compressor assembly 14 and motor stator 16 are completely independent of each other. Compressor assembly
The above-mentioned motor rotor 18 for driving the motor 14 is press-fitted or heat-shrink-fitted to the lower end of the crankshaft 82, and is disposed in the center hole (rotor receiving hole) 126 of the motor stator 16. .

A unique cam drive is used to convert the rotational drive force imparted by the electric motor to the crankshaft 82 into the reciprocating motion of the piston 94 in the electric compressor 10. This new cam drive allows the cylinder and head mechanism to be retained within the generally cylindrical area defined by the motor stator 16 while providing a discharge gas discharge time that is substantially longer for the connecting rod piston drive. Even longer than is typically achieved by a mechanism or Scottyoke drive mechanism is possible. As shown in FIG. 1, the crankshaft 82 includes an eccentric portion 128, which is eccentric to the cam member 132 which is supported in the journal hole 106 of the piston 94, as shown clearly in FIG. It is supported by 130.

The operation system of this cam drive device will be described with reference to FIG. 6-13. In FIG. 6, the piston 94 is at the bottom dead center.
At this position, the rotation axis 134 of the cam 132 and the crankshaft eccentric portion 12
The axis 136 of 8 and the axis of rotation 138 of the crankshaft 82 are all aligned along the line of motion of the piston 94, and the axis of rotation 1 of the cam 132
32 is farthest from the cylinder hole 72, and the eccentric part 128
Axis 136 of cam 132 and axis 138 of crankshaft 82.
Between As the crankshaft 82 is rotationally driven in the clockwise direction as shown, the axis line 136 of the crankshaft eccentric portion 128 is moved laterally from the aligned position. Since the lateral movement of the cam member 132 is constrained by the piston 94, the cam member 132 is initially counterclockwise so as to allow the above-mentioned lateral movement of the crankshaft eccentric portion 128. It is driven to rotate. As the crankshaft 82 continues to rotate in the clockwise direction, the cam member 132 rotates until maximum lateral movement of the axis 136 of the crankshaft eccentric 128 is achieved, and the maximum lateral direction of the axis 136 described above. Movement is 90 from bottom dead center as shown in Fig. 8.
Occurs during rotational displacement of 1 degree. At this point, the cam member 132 starts rotating in the clockwise direction by reversing the rotation direction because the amount of lateral displacement of the axis line 136 of the eccentric portion 128 decreases.
Therefore, both the crankshaft eccentric portion 128 and the cam member 132 rotate in the same direction until the maximum lateral displacement in the opposite direction of the axis 136 that occurs at a position 90 ° from the top dead center is achieved. (See Figure 12). The actual displacement angle θ of the cam member 132 is related to the respective turning radii R ₁ and R ₂ , and the following equation holds.

Where R ₁ is the axis line 138 of the crankshaft 82 and the axis line 13 of the eccentric part 128.
6, the radius between 6 and R ₂ is the axis 134 of the cam member 132 and the eccentric portion 128.
Is the radius between the axis 136 and. Therefore, R ₂ is 0
Greater than (zero) and R ₁ is less than R ₂ (eccentric part 128
This is inevitable because the axis line 136 cannot be actually located on the peripheral edge of the cam member 132. ) As long as cam 132 is 1
Rotate by less than 80 °. In order to maintain the lateral load on the piston 94 and thus the friction loss to a reasonable level, R ₂ should be at least 1.75.
It is believed desirable to choose to be equal to or greater than R ₁ .

FIG. 14 shows a plot of piston displacement percentage as a function of crankshaft angular displacement for various drive connection schemes. As can be seen from the figure, the time required for the piston to displace up to 75% of the maximum displacement (100% corresponds to top dead center) or beyond (this is directly proportional to the rotation angle of the crankshaft). Is larger than that with a relatively short connecting rod drive mechanism, and is actually larger than with a relatively long connecting rod mechanism or a simple string motion of a Scottyoke mechanism (SYM). Is quite large. Therefore, using the illustrated cam drive, the maximum size of the compressor and head along the line of motion of the piston should not be greater than the diameter of the motor stator, and a circular shell of minimum size should be used. While enabling this, the time available for expelling the discharge gas from the compression chamber can be significantly increased.

An oil sump 140 is provided at the bottom of the lower shell portion 22 for lubricating the electric motor 10, and the conical end of the oil take-out pipe 142 is projected into the oil sump 140. The upper end portion of the oil take-out pipe 142 has a cylindrical shape, and is attached to the lower end of the crankshaft 82 so as not to rotate relative to it. As is well known to those skilled in the art, the centrifugal force imparted to the lubricating oil in the oil take-out pipe 142 by the rotation of the oil take-up pipe 142 causes the lubricating oil to be upwardly and radially biased to the crankshaft. Oil passage 144 provided in 82
Is pumped through. The oil passage extending in the axial direction
Lubricating oil is provided to the main bearing 80 and to the bearing surface between the crankshaft eccentric portion 128 and the cam member 132 by radially outwardly extending passages 146 and 148 in communication with the 144. Is guided. A pair of passages 150 and 152 circumferentially spaced to lubricate the boundary area between the cam member 132 and the piston 94, as shown in FIG. Has been formed.

In order to ensure that a proper amount of lubricating oil is supplied to the upper bearing surface of the cam, the crankshaft eccentric
Exhaust passage 154 extending radially inward from the outer surface of 128
Is provided so as to communicate with the oil passage 144 in a direction slightly below the upper end of the cam member 132 and across the upper end of the oil passage 144 in the axial direction. As shown in FIGS. 1 and 15, a notch groove 156 is provided on the upper edge of the bearing surface on the cam member 132.
The notch groove 156 is arranged around the movement axis of the piston 94 on the non-load side of the bearing surface (that is, the side opposite to the cylinder hole 72) over a range of about 180 ° in the circumferential direction. Therefore, when the crankshaft 82 rotates the eccentric portion 128, the passage 154 communicates with the notch groove 156 periodically, and as shown in FIG. 16, the piston movement in which the crankcase pressure is lower than the average discharge pressure region is performed. During the process, exhaust is provided from the oil passage 144 to the crankcase. This rotary valve action exposes the upper end of the axial oil passage 144 to a relatively low pressure, which promotes the flow of lubricating oil through the oil passage 144. Since the exhaust passage 154 extends along the direction crossing the rotation axis of the crankshaft, it is difficult for the lubricating oil to be sucked into the crankcase during normal operation.

The compressor housing is configured to prevent lubricant from accumulating in the crankcase due to leakage from the bearings and / or suction through the exhaust passage 154 and to prevent excessive pressure in the crankcase. A lubricating oil return port 158 is provided on the lower flange portion 60 of the main body 56. It is preferable to provide a relatively small notch groove or recess 160 around the crankcase side of the return port 158 to provide a collecting and storing of lubricating oil.

A plastic tube 162 extending downwardly from the lubricating oil return port 158 is provided to minimize mixing of the lubricating oil with the intake gas while returning to the oil sump 140. In this tube 162, the lower end side of the tube 162 is an outer shell part.
It is leaned toward 20 and is slightly bent so that the lower end opening of tube 162 is located just above one of the spaces 122 between the motor stator 16 and the shell portion 22. As shown, the lower end of the pipe 162 is cut at an angle so that the return lubricating oil is discharged toward the outer shell portion 20 and moves away from the intake gas.

Lubricating oil return port 158 and tube 162 have a minimum diameter within the limits that allow the required oil flow, thereby minimizing the pressure differential between the crankcase and the lower portion of shell 12. It is desirable to be something like keeping. Also, the tube 162 is preferably relatively long in length relative to its diameter to provide a relatively high dynamic discharge resistance.

The present invention also includes a unique and novel assembly method that seeks to quickly and easily assemble the various components to form a compact and efficient electric compressor.
Referring to FIG. 18, the first step in assembling the electric compressor 10 is to finish the compressor body 56 and the outer diameter of the main bearing 80. When this is done the main bearing
The 80 is press fit into the hole 78 in the main body 56 which is the compressor housing. Thereafter, the inner diameter of the bearing 80 is machined to the final tolerance and the bearing surface provided within the bearing 80 is positioned concentrically with the compressor housing 56.

Then insert the piston 94 into the cylinder bore 72 and into the compressor housing.
Inserted through a relatively large hole 74 in 56, and then a subassembly with crankshaft 82, cam member 132 and counterweight 90 in the compressor housing and piston 94 through holes 88 and 106, respectively. Insert it in the rod part of.

The next step is to assemble the valve plate assembly 108 and head 110 to the compressor housing 56. Because of this assembly
And to ensure a minimum re-expansion volume between piston 94 and valve plate assembly 108, as shown in FIG.
It is first necessary to advance piston 94 to top dead center where 94 will project a small distance P from surface 164 of housing 56. The distance P is then measured and is set to the desired desired preset gap (typically 0.006 inches-about 1.5 mm) which should be provided between the top end of the piston 94 and the valve plate 108.
-Order)). This total is the housing
Required thickness G of gasket 166 located between 56 and valve plate 108
give.

The diameter A of the housing 56 is then measured along a straight line transverse to the direction of movement of the piston 94. Also same housing
The maximum width B of 56 is measured in the direction of movement of piston 94. The thickness G of the gasket 166 and the thickness C of the valve plate 108 are added to the measurement width B.
And the maximum thickness D of the head 110 is added. This sum (G + B + C + D) is then subtracted from the diameter A measured as above. To ensure a firm clamping action, it is desirable that the overall dimensions of the compressor assembly 14 in the direction of movement of the piston 94 be slightly larger than the diameter A. This is the planned clearance value (typically 0.006 inches-about 1.5 m
m) is added to the difference between A and G + B + C + D. The value thus obtained is the required thickness T of the head gasket 168 to be located between the valve plate 108 and the head 110.

Once such a gasket thickness T has been selected, the housing reed valve pin and locating pin (not shown) are then first inserted into the appropriate openings provided in the surface 164 of the housing 56 to cause the housing 56 to The valve plate device shall be installed on top. The preselected valve plate gasket 166 is then placed on the housing 56 positioned by the locating pins and the suction lead and valve plate 108 are subsequently placed. The discharge valve pin, discharge valve and backing (not shown) are then assembled to the valve plate 108 and the preselected head gasket 168 is subsequently mounted. The head 110 is then placed on the housing 56 and the resulting assemblies are clamped together and press fit onto the upper shell portion 20.

As shown in FIG. 19, the motor stator 16 is press-fitted to the outer shell portion 22 on the lower side. Center hole 126 of this motor stator 16
On the other hand, in order to precisely position the crankshaft 82 in a concentric arrangement, a mandrel 170 for positioning is inserted into a hole between the stator 16 and the crankshaft 82. In order to allow adjustment to align the crankshaft 82 correctly,
The entire peripheral area of the upper and lower outer shell portions 20, 22 may partially cover the flanges 24, 26 to provide a slight gap. Next, the flanges 24 and 26 are tack welded at two opposite positions, then the orientation of the assembly is changed by 90 °, and tack welding is performed again at the two opposite positions to restrain the position of the assembly. Next, the entire peripheral edges of the flanges 24 and 26 are welded.

The thrust washer 172 and the holder 174 for the washer 172 (above, FIG. 1) are assembled to the crankshaft 82, and then the motor rotor 18 is heat-shrink-fitted to the crankshaft 82. The oil take-out pipe 142 is press-fitted onto the crankshaft 82, and then the bottom portion 28 is welded and fixed to the lower end of the outer shell portion 22 on the lower side.

Then, a pair of annular gaskets 176 and 178 shown in FIG.
From the upper side flange portion 58 of the compressor housing 56 to the periphery of the discharge gas outlets 50 and 52 that open to the outside, and the lower members 44 of the discharge muffler 32 are flanged by a plurality of bolts 54. Fix to 58. Next, the baffle member 48 is fixed to the assembly using the nut 180, and then the upper member 34 of the muffler 32 is assembled, where the upper and lower muffler members 34 and 44 are simultaneously attached to the upper end of the upper outer shell portion 20. And welded to both parts at the same time
34 and 44 are also welded. The central portions of both members 34 and 44 of the discharge muffler 32 are also welded to each other, and the assembly is completed.

The resulting compressor is a hermetic electric compressor that is extremely compact and easy to assemble, requiring only a minimal number of parts and 3 parts to restrain the parts in the assembled operating condition. Only separate fasteners for books are needed.

FIGS. 21 and 22 show an embodiment in which another mechanism for assisting the oil pumping for circulating the lubricating oil is provided for the bearing portion. In this embodiment, a smaller diameter first oil passage 144, which is provided in the crankshaft 82 and communicates with the upper end portion of the oil passage 144 in the axial direction in the radial direction of the oil passage 144, along the axial direction. 2 passage 182, crankshaft 82
The second passage 182 is formed in the crankshaft 82 so that the oil passage 144 always communicates with the inside of the crankcase.
It opens to the top of the. In order to maintain the pressure in the crank chamber at the suction pressure in the electric motor installation space or at a pressure lower than that, a pair of openings 184 and 186 are provided in the lower flange portion 60 of the housing 54, and the openings 184 and 186 are provided at the openings 184 and 186. A pressure-responsive reed valve 188, which is arranged so as to overlap with it and is attached to the flange portion 60 at one end, is additionally provided. Therefore, as the piston 94 moves back toward the crankcase during the suction process, the pressure that increases in the crankcase is increased by the opening 18
Escaped through 4,186. Then, as the piston 94 moves away from the crankcase during compression, the valve
188 closes and the pressure in the crankcase drops. Oil such as leak oil in the crankcase is returned through the openings 184, 186, and therefore the returned oil is guided to the oil sump 140 through the space 122 between the outer shell portion 22 and the motor stator 16. A baffle tube 190 is provided to minimize mixing of the lubricating oil with the suction gas. The openings 184, 186 are preferably relatively large so as to provide an opening cross-sectional area sufficient to allow exhaust (pressure relief) from within the crankcase.
It is important when the pressure relief valve of the discharge muffler opens and discharges the discharge gas into the crankcase.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing an example of a hermetic electric compressor according to the present invention. FIG. 2 is a transverse sectional view taken along the line 2-2 in FIG. FIG. 3 is a cross-sectional view taken along the line 3-3 of FIG. FIG. 4 is a cross-sectional view taken along the line 4-4 of FIG. FIG. 5 is a perspective view showing a piston used in the electric compressor shown in FIG. Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 11, Fig.
12 and 13 are schematic cross-sectional views sequentially illustrating the operation of the drive unit provided in the hermetic electric compressor shown in FIG. FIG. 14 is a graph showing the piston displacement ratio as a function of the crankshaft displacement angle for the drive unit used in the present invention and another drive unit. FIG. 15 is a cross-sectional view showing the upper end of the crankshaft in the electric compressor shown in FIG. 1, and the cross section is taken along the line 15-15 in FIG. FIG. 16 is a graph showing pressure fluctuations as a result of reciprocating motion of the piston in the crankcase of the electric compressor shown in FIG. FIG. 17 is an exploded perspective view of a part of the compressor assembly shown in FIG. 1 and illustrates a method of selecting a head gasket. FIG. 18 is an exploded vertical sectional view of a part of the compressor assembly shown in FIG. 1 and illustrates a method of assembling the upper side portion of the compressor assembly. FIG. 19 is an exploded vertical sectional view of the electric compressor shown in FIG. 1 and illustrates a method of assembling the upper side portion and the lower side portion of the compressor. FIG. 20 is an exploded vertical sectional view of a part of the electric compressor shown in FIG. 1 and illustrates a method of assembling the discharge muffler provided in the compressor. FIG. 21 is a partial vertical cross-sectional view showing another example of the electric compressor according to the present invention, showing another example of the pressure relief mechanism from the inside of the crankcase. FIG. 22 is an enlarged partial sectional view of the pressure relief mechanism shown in FIG. 21, and the cross section is taken along line 22-22 in FIG. 10 …… hermetic type electric compressor, 12 …… outer shell, 14 …… compressor assembly, 16 …… motor stator, 18 …… motor rotor, 20,2
2 …… Cylindrical shell part, 24,26 …… flange part, 28 …… bottom part, 32 …… discharging muffler, 34 …… annular member, 44 …… bottom members, 46 …… silence cavity, 48… … Butful material, 54 …… Bolt, 56 …… Main body (compressor housing), 58,60 ……
Flange, 62, 64 ... Side wall, 66 ... Cylinder wall, 72 ...
… Cylinder hole, 74 …… Large diameter hole, 76 …… Suspended part, 80 …… Bearing, 82 …… Crank shaft, 90 …… Balance weight, 94
...... Piston, 96,98 …… Side wall, 104 …… Band, 106
...... Journal hole, 108 …… Valve plate assembly, 110 …… Head, 114 …… Suction chamber, 116 …… Discharge chamber, 122 …… Space, 124
…… Suction port, 126 …… Center hole (rotor receiving hole), 128 ……
Eccentric part, 130 ... Eccentric hole, 132 ... Cam member, 134 ... Cam member axis line, 136 ... Eccentric part axis line, 138 ... Crank shaft lines, 140 ... Oil sump, 142 ... Oil take-out pipe, 144 …… Oil passage, 154 …… Exhaust passage, 156 …… Notch groove, 158 …… Lubricant oil return port, 162 …… Pipe, 166 …… Gasket, 168 …… Gasket, 170 …… Mandrel, 182… … Passage, 184,186 …… Opening, 188 …… Pressure responsive reed valve, 190 …… Baffle tube.

Front Page Continuation (72) Inventor Jiyoung Paul Elsson United States 45365 Sidony-Ohst Robin Woods 316, Ohio 316 (72) Inventor Derip Sadhaka Sasse United States 45365 Sydney-Westminster, Ohio --Coat 2110 (72) Inventor Alle Berner Miyua United States 45365 Sidney, Hill Drive, Ohio 14195 (72) Inventor Walter Thomas Glasbaufe United States 45365 Sidney, Ohio 5359 State Route 29 (56) Bibliographic Reference Sho 56-63875 (JP, U) JP 47-9832 (JP, B1)

Claims (22)

[Claims] 1. A refrigeration compressor, comprising: an outer shell, a compressor assembly installed in the outer shell, and a motor means having a stator and a rotor, wherein the outer shell is a stator. Motor means connected to the compressor assembly for supporting the compressor and being driven by the rotor to drive the compressor assembly; and an oil sump provided in the outer shell for compressing the compressor. A lubricating oil supply means for guiding lubricating oil to the machine assembly, and a discharge muffler for silencing the discharge gas discharged from the compressor assembly, the discharge muffler on the opposite side of the motor means from the compressor assembly. A first plate member disposed adjacent to one end face, the first plate member having an annular convex peripheral edge along an axial direction of the outer shell at an outer peripheral end, and fixed to one end of the outer shell. To form the outer end wall of the outer shell A second plate member, the first plate having an annular convex peripheral edge at an outer peripheral end, the annular convex peripheral edge protruding toward the first plate member and fixed by being superposed on the convex peripheral edge of the first plate member. A second plate member forming a silencing cavity for receiving a discharge gas from the compressor assembly together with the member, the second plate member having a convex peripheral edge located on an extension line of a peripheral wall of the outer shell. On the other hand, the convex edge of the first plate member is overlapped with the inner surface of the outer shell and the inner surface of the convex edge of the second plate member so as to overlap each other, and the convex edge of the first and second plate members is arranged. And a discharge muffler formed by welding and fixing each other and the outer shell together from the convex peripheral edge of the second plate member and the outer surface side of the outer shell. The discharge gas outlet of the compressor assembly is provided with the discharge muffler. Opening at the above end face In addition, the opening provided in the first plate member directly overlaps the discharge gas outlet with respect to the one end surface of the compressor assembly, and the first plate member is provided in the silencing cavity from the discharge gas outlet. A refrigeration compressor engaged such that the flow of discharge gas into the first plate member is through the opening. 2. The refrigeration compressor according to claim 1, wherein the first plate member is fixed to the one end surface of the compressor assembly. 3. The refrigerating compressor according to claim 2, wherein a baffle member is provided in the sound deadening cavity, and discharge gas flowing into the sound deadening cavity collides directly with the baffle member. A refrigerating compressor, which is arranged and provided, and the baffle member is fixed to the one end surface of the compressor assembly together with the first plate member by a common fastener. 4. The refrigerating compressor according to claim 1, wherein the second plate member has an annular outer convex edge projecting toward the first plate member as an inner peripheral end. While having an annular convex shape, an inner convex rim protruding toward the second plate member and airtightly fitted and held to the other convex rim at the center of the first plate member. A refrigeration compression in which the silencing cavity is formed in an annular shape by providing an inner convex peripheral edge with a projecting end sealed so as to form an outer end wall of the outer shell together with a second plate member. Machine. 5. The refrigeration compressor according to claim 1, wherein the compressor assembly is reciprocably provided in a housing forming a crankcase and a cylinder defined by the housing. And a main bearing means for rotatably supporting a crankshaft driven by the motor means in the housing, the crankshaft being operatively connected to the piston via the piston bearing means. Is immersed in the oil sump at the lower end of the crankshaft, and the lubricating oil supply means is arranged in the crankshaft to guide the lubricating oil from the oil sump to the main bearing means and the piston bearing means. An oil passage provided along the axial direction, opened in the crankcase and located on the opposite side of the oil sump An exhaust passage provided in the crankshaft in communication with one end of the oil passage, and exhaust valve means arranged between the crankcase and the inside of the outer shell, wherein the piston reciprocates. In response to the pressure increase in the crankcase due to the movement of the crankcase, the exhaust gas is discharged from the crankcase to the inside of the outer shell so that the pressure in the crankcase becomes substantially equal to or lower than the pressure inside the outer shell. Maintaining and keeping the pressure at one end of the oil passage lower than the pressure inside the outer shell via the exhaust passage, promoting the flow of oil supplied to the bearing means via the oil passage. Refrigeration compressor equipped with exhaust valve means. 6. The refrigeration compressor according to claim 5, wherein the exhaust valve means is configured to promote return of oil from the crankcase to the oil sump. Machine. 7. The refrigerating compressor according to claim 6, further comprising: an oil guiding means arranged around the exhaust valve means, the lubricating oil being returned from the crankcase to the oil sump. A refrigeration compressor provided with oil guiding means for guiding the lubricating oil so as not to mix with the suction gas supplied from a suction gas inlet opening inside the outer shell. 8. A refrigeration compressor according to claim 5, wherein the exhaust valve means connects the inside of the crankcase with the inside of the outer shell, and selectively closes the opening. Compressor for refrigeration equipped with pressure responsive valve means for 9. A refrigeration compressor according to claim 1, wherein said compressor assembly is supported on a housing forming a substantially closed crankcase and a main bearing in said housing. A crankshaft driven by the motor means, a piston connected to the crankshaft so as to be driven by the crankshaft, the piston including bearing means at a connecting portion, and the oil sump Passage means provided in the crankshaft for guiding the lubricating oil from the above to the main bearing and the bearing means, the passage means including an opening into the crankcase, and the reciprocating movement of the piston. Exhaust valve means for selectively communicating the inside of the crankcase with the inside of the outer shell when the pressure inside the crankcase increases, Exhaust valve means for maintaining the pressure in the rank case at a value less than or equal to the pressure inside the shell to facilitate the flow of lubricating oil supplied to the main bearing and bearing means via the passage means; A compressor for refrigeration equipped with. 10. The compressor for refrigeration according to claim 1, wherein the compressor assembly is reciprocably provided in a housing forming a crankcase, and a cylinder defined by the housing. And a main bearing means for rotatably supporting a crankshaft driven by the motor means in the housing, the crankshaft being operatively connected to the piston via the piston bearing means. Is immersed in the oil sump at the lower end of the crankshaft, and the lubricating oil supply means is arranged in the crankshaft for guiding the lubricating oil from the oil sump to the main bearing means and the piston bearing means. The oil passage is provided along the axial direction, and the oil is opened to the outside through the side wall of the crankcase. And a valve means for selectively communicating the exhaust passage with the inside of the crankcase, the exhaust passage being provided in the crankshaft on the opposite side to the oil passage. . 11. The refrigerating compressor according to claim 10, wherein the valve means has one crankshaft.
A refrigeration compressor provided with a shutoff means for shutting off the exhaust passage in a part of a rotation range during rotation. 12. The refrigeration compressor according to claim 10, wherein the piston bearing means includes a notch groove extending in the circumferential direction at one end of the piston bearing means, and the exhaust passage has the notch groove in the crankcase. A refrigeration compressor which is said to be selectively communicated with each other through a notch groove. 13. A compressor for refrigeration according to claim 1, wherein the compressor assembly is supported by the outer shell, and the stator of the motor means is spaced apart from the compressor assembly. And a compressor for refrigeration, which is placed in a space and is supported by the outer shell independently of the compressor assembly. 14. A refrigeration compressor as set forth in claim 13, wherein said compressor assembly comprises a body and a head, and said outer shell is a single unit for restraining said head on the body. A compressor for refrigeration configured as described above. 15. The refrigeration compressor according to claim 13, wherein the discharge muffler is attached to the body by a fastener, and the fastener is used in the compressor. Refrigeration compressor, the only fastener. 16. The compressor for refrigeration according to claim 1, wherein the stator of the motor means has a substantially cylindrical shape, and the outer shell is substantially the same as the outer diameter of the stator. Formed to have the same inner diameter and engaged with the outer peripheral surface of the stator, and the compressor assembly is attached to a cylinder, a piston disposed in the cylinder, and the piston for driving the piston. Formed to have a substantially cylindrical shape including a crankshaft connected to the motor means so as to be driven by the motor means, so that the maximum outer diameter of the compressor assembly is equal to the inner diameter of the outer shell. A refrigeration compressor set to a value that does not exceed the outer diameter of the stator so that it can be made smaller within the limits required to receive the stator of the motor means. 17. The refrigeration compressor according to claim 16, wherein the valve assembly and the cylinder head are superposed on the cylinder, and the outer shell restricts the position of the cylinder only by the outer shell. A freezing compressor. 18. The refrigerating compressor according to claim 1, wherein the compressor assembly is directly engaged with the outer shell and supported by the outer shell, and the compressor assembly is provided. A housing in which a solid body forms a cylinder, a piston reciprocally provided in the housing for compressing a refrigerant, the piston including a connecting portion having an opening, and rotatable by a bearing means in the housing. A supported crankshaft having a eccentric portion, and a cam member rotatably provided in the opening of the connecting portion, the eccentric opening supporting the eccentric portion of the crankshaft. A cam member is provided, and the stator of the motor means is directly engaged with the outer shell to be supported by the outer shell, and the stator is supported by the crankshaft. It has a bore for supporting the rotor which had been lifting, configured refrigerating compressor so as to reciprocate the piston in the cylinder by the motor means. 19. The refrigeration compressor of claim 1, wherein the compressor assembly is supported within the first shell portion of the shell and is rotatable from one end. A drive shaft, wherein the stator of the motor means is supported in the second shell portion of the shell and supports the rotor fixedly mounted on the drive shaft. A through hole extending along the axial direction is provided, and the first outer shell portion and the second outer shell portion are arranged in a radial direction so that the rotor is positioned in the through hole, and are aligned with each other. A refrigeration compressor fused and provided with a uniform gap between the rotor of the motor means and the stator. 20. The refrigeration compressor according to claim 19, wherein the first outer shell portion and the second outer shell portion each have an annular shape extending outward in the radial direction. A refrigeration compressor having a flange portion and these flange portions welded to each other. 21. The refrigeration compressor according to claim 20, wherein the flange portions have a slight interval between them in the circumferential direction, and the flange portions are mutually isolated. A refrigeration compressor in which the gap is welded and sealed so as to be fixed hermetically. 22. The refrigeration compressor according to claim 19, wherein the uniform void is held only by the welding.