JPS6027789A - Reciprocating type compressor and method of assembling said compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a compressor, particularly a hermetic reciprocating refrigerant compressor, and a method for assembling the compressor.

Hermetic refrigeration compressors are used in various ways in residences and commercial facilities. In all of these applications, the compressor is required to achieve reliable operation over long periods of time, requiring little or no maintenance, and as economically as possible. In order to obtain reliable and economical operation of τ over a long period of time, and which requires no maintenance at all, the compressor should have as little l!L on its parts as possible, and should be It is highly desirable to have a design that is both easy to use and as compact as possible.

This invention provides a hermetic type reciprocating compressor which takes a unique approach to achieve the above-mentioned conflicting objectives.

In this invention, the compressor assembly (compression mechanism) and motor stator are supported independently and directly by the outer shell, eliminating the need for a separate support mechanism and facilitating assembly. . The compressor assembly is also configured to utilize an outer shell with the compressor body to restrain the head and valve assembly in an assembled relationship, thereby eliminating the need for separate fasteners. ''ttt shall be completely eliminated. A unique, simple, straight cam drive system is provided, which is essentially a compressor based on the rather complex Scotchoke drive system. This significantly improves the operating efficiency of the compressor by allowing a longer time for the compressed refrigerant to evacuate from all cylinders compared to the cam drive mechanism. The discharge time can be provided by a cam member which functions as a piston pin and connecting rod and is supported in a hole in the piston.

This allows the maximum dimensions of the compressor to be reduced to a size greater than the diameter of the motor stator, allowing the compressor assembly to be placed in a relatively small circular shell. The use of an integral piston and continuous rod also further reduces the number of parts required and assembly time.

The compressor according to the invention is provided with an improved discharge muffler which has an inlet connected directly into the compressor housing and which channels the discharge gas from the compression chamber to the discharge muffler. The discharge muffler also forms part of the shell, and since compressor 1a is fixedly supported in the shell, it is not connected to other parts of the refrigeration system. Piping vi for supplying the entire compressed refrigerant - enables direct connection.

A unique method for assembling the compressor of the present invention is also disclosed, which method includes assembling the compressor and motor stator into separate shell sections, and then combining both shell sections. It is configured to be precisely positioned and connected by welding so that no distortion occurs due to the heating caused by welding. The assembly method also provides for a suitable thickness of the head gas foot to ensure positive sealing of the head and valve assembly to the compressor body when the compressor assembly is press-fit into the shell. It also includes a method of selection.

In order to obtain positive and sufficient lubrication of the compressor according to the invention, in the embodiment - the upper end of the oil passage along the axial direction t = % selectively communicates with the qualitatively closed crankcase. A low-return valve is used to generate a pressure difference and sound in the oil passage to promote the flow of lubricating oil. In other embodiments, 1 gc! The oil passage will be in continuous communication with the crankcase, and pressure will be released from the crankcase to the inside of the outer shell through an opening equipped with a pressure-responsive valve. Therefore, in the low-pressure cycle resulting from the reciprocating motion of the compressor, the oil flow through the oil passage T is facilitated. From the above, the present invention greatly reduces the number of necessary parts. Therefore, it is manufactured at low cost and has high reliability.
It also provides a highly original and novel compressor that is extremely compact and provides high operating efficiencies not heretofore achievable with compressors of comparable size.

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

Referring to the drawings, a hermetic electric compressor in accordance with the present invention is illustrated generally by the reference numeral 10 in Figures 1-15.

The electric compressor IO has a hermetically sealed, segmented shell 12 within which a motor is driven, including a motor stator 16 and a motor rotor 18t. The interlocking compressor assemblies 14 are independently supported.

The outer shell '12, which is formed by being divided into a plurality of parts, includes vertically elongated, substantially circular parts (cylindrical parts) 20 and 22 on one side and a lower part, and each of these cylindrical outer shell parts 20 and 22 24 has a flange projecting radially outward.
p 26 t", these crank parts 2
4.26 is made of a material that can be abutted against and fixed to these gold conductors. A bottom portion 28 is fixed to the lower end of the lower cylindrical shell portion 22, and a plurality of installation legs 8 (1, It is integrally formed so as to protrude outward in the radial direction.

A discharge muffler 32 is attached to the upper end of the upper cylindrical shell portion 20 and forms a cover for the top end of the shell 120. This discharge muffler 32 has inner and outer convex peripheral edges 36 and 38.
The entire annular member 84 is provided with a convex peripheral edge 36.88.
are overlapped with each other so that an annular sound-dampening cavity 46 is formed between the inner and outer convex peripheral edges 4 (1, 42) of the lower part 44 of the discharge muffler 32 and both of the above-mentioned members 84, 44. An arcuate baffle member 48 having a generally inverted U-shaped cross-section is located within the muffling cavity 46 at a pair of spaced discharge gas inlets 50° 52 (
3 and 17), and are fixed by a plurality of threaded fasteners (bolts) 54.

As clearly shown in FIG.
Lower member 44t - also used to secure to the compressor 14. The compressor 14 includes a main pod (compressor housing) 56 having upper and lower generally circular flange portions 58 and 60 spaced apart from each other on one end side. , interconnected by a pair of substantially parallel mirror-symmetric chord-shaped side walls 62, 64 and a cylinder wall 66 extending therebetween in a direction substantially orthogonal to the side walls 62, 64. There is another.

As clearly shown in FIG. 4, the cylinder wall 66 includes tapered surfaces 68 and 70 at each end thereof, which surfaces 68 and 70 form the upper cylindrical shell portion of the shell 12. The crank portion 60 on the lower side that is in close contact with the inner circumferential surface of 20
and is shaped so as to cooperate with the lower member 44 of the discharge muffler 32 to form a substantially closed crankcase. A cylinder hole 72 is generally drilled through the cylinder wall 66, and this cylinder hole 72 is formed in the side wall 66.
2°64 and the large diameter hole 74 which is divided into groups at the lower flange portion 58.60 and are opposite to each other at t9.

The lower flange portion 6° of the main pod 56 supports a truncated conical suspension portion 76 that forms an open lower portion 8, and the open lower portion 8 rotatably supports a crankshaft 82. It is designed to receive an elongated stepped bearing 80. As shown in FIG. 1, the bearing 80 includes an axial thrust shoulder 84 that is capable of abutting an annular shoulder 86 on a crankshaft 82. As shown in FIG.

A relatively large-diameter opening 88 is provided through the upper flange portion 58, and this opening 88 is arranged concentrically with the above-mentioned opening lower portion 8, and is connected to the extension portion &' of the crankshaft 82.
c A press-fitted counterweight 90 is rotatably housed.

A piston 94 is disposed in the cylinder hole 72 so as to be reciprocally movable, and the piston 94 is reciprocally movable.The piston 94 is provided with a drive shaft such that the piston 94 can be moved relative to the crankshaft 82, as clearly shown in FIG. A pair of elongated side walls 96 and 98 are arranged parallel to each other and spaced apart from each other.
Contains. lll'l The outer surface of the wall portion 96.98 is
It is formed on a cylindrical surface that comes into close contact with the side wall of the large-diameter hole 74 in the compressor housing, and the cover 1 piston 94 is supported so as to be able to reciprocate laterally. A pair of curved arms 100.1 between the above-mentioned side wall portions 96.98.
02 extends rearward and northward and downward, respectively, and the outer surfaces of these curved arms 100 and 102 are also formed into cylindrical surfaces so as to be in close contact with the side walls of the large diameter hole 74. , serves to support and guide the reciprocating piston 94.Curved arm 100.1 (+2
Between the sidewalls 96 and 98 is an arched strip 10.
4, the strip 104 cooperates with the sidewall 96° 98 to form a relatively large diameter journal hole 106' for drivingly connecting the piston 94 to the crankshaft 92. is forming. The strip 1O-4 can be formed to become narrower towards the non-load side of the connection so as to reduce the weight of the piston 140 without sacrificing reliability. Also piston 9
4, the cross-sectional area of the curved arms 100, 102 is smaller than the side wall portion 96.
It can be machined substantially smaller than the cross-sectional area of 98°.

The valve plate assembly 108 and head 110 are connected to the cylinder bore 72.
They are arranged so that they overlap the outer edges in the radial direction. As clearly shown in FIG.
This outer surface 112 shape is configured such that the head 110 is tightly anchored and held in place by the compressor housing without any additional coupling. Valve plate assembly 108 is also shown extending chordally between the sidewalls of shell portion 20 and cooperates with head 110 to prevent fluid leakage between the crankshaft and a lower portion within shell 12. To prevent. The head 110 includes a suction chamber 114, and this suction chamber 114 has an opening at its lower end.
It communicates with the motor room (the installation space for the electric motor) through the
Intake gas is supplied from there to the cylinder hole 72. Also included within the head 110 is a discharge chamber 116 that receives discharge gas from the cylinder bore 72 and directs it through the discharge gas ports 50 and 52 described above to the discharge muffler 32. The valve plate is, of course, provided with suitable boats and lubes for controlling the flow of fluid into and out of the cylinder bore.

The stator 16 of the electric motor described above is designed to be press-fitted or heat shrink-fitted into the lower cylindrical shell portion 22 of the outer shell 12 so as to be supported only by the outer shell portion 22; For this reason, as clearly shown in FIG. 2, the outer shell portion 22 has a substantially rectangular cross-sectional shape with all arcuate notches at the four corners so as to tightly engage with the side wall of the outer shell portion 22. ing. In order to prevent excessive stress from being applied to the outer shell portion 22 and causing distortion in the shape of the portion 22, a periphery of the motor stator 16 is provided at the intersection of the above-mentioned notch and the flat side wall surface. A cut groove 12-Ot- is provided for relief. A space 122 formed between the motor stator 16 and the outer shell portion 22 between adjacent corners 118 allows suction gas to enter the cylindrical portion 16 through the inlet 1241 to cool the electric motor. It will be circulated so that

As described above, the electric compressor 10 includes an upper outer shell portion (an upper cylindrical portion of the outer shell 12) 20 and a compressor string solid body 14 that is directly supported and fixed to the upper shell portion 20. , and the motor stator 16 directly supported and fixed within the lower shell portion (lower cylindrical portion of the outer shell 12) 22, and these Compressor assembly 14 and motor stator 16 are completely independent of each other. The motor rotor 18 described above for driving the compressor assembly 14 is located at the lower end of the crankshaft 82 .

In the electric compressor lO, the crankshaft 82 is
A unique cam drive is used to convert the rotational drive force applied to the piston 94 into reciprocating motion of the piston 94. This novel cam drive allows the cylinder and head mechanism to be held within a generally cylindrical area defined by the motor stator 16, while allowing the evacuation time of the discharge gases to be substantially longer than the connecting rod piston drive. The machine configuration allows for even longer shaft lengths than typically achieved with Scotch drive mechanisms.As shown in FIG.
As clearly shown in FIG. 4, 8 is supported in the eccentric hole 180KJ of the cam member 182, which is supported in the journal hole 106 of the piston 94.

The operating system of this cam drive device will be explained with illustrations in FIGS. 6-18. In FIG. 6, piston 94 is at bottom dead center. In this position, the rotational axis 184 of the cam 1B2, the axis 186 of the crankshaft eccentric portion 128, and the rotational axis 188 of the crankshaft 82 are all aligned with the line of motion of the piston 94, and the rotational axis 182 of the cam 1B2 is aligned with the cylinder hole. 72, and the axis 186 of the eccentric portion 128 is between the axis 1B4 of the cam 1B2 and the axis 188 of the crankshaft 82. As crankshaft 82 is rotated clockwise as shown, axis 136 of crankshaft eccentric 128 is moved laterally from the aligned position described above. Since the lateral movement of the cam member 1g2 is restrained by the piston 94, the cam member 18
2 is first rotated in the counterclockwise direction so as to permit the lateral movement of the crankshaft eccentric portion 128 as noted. As the crankshaft 82 continues to rotate clockwise, the cam member 182 rotates toward the crankshaft eccentric portion 1.
28 until maximum lateral movement of axis #186 is achieved, with the maximum lateral movement of axis #136 occurring at a 90 degree rotational displacement from bottom dead center as shown in FIG. At this point, the cam part @132 is aligned with the axis 18 of the eccentric part 128.
Since the amount of lateral displacement of 6 is decreasing, the direction of rotation is reversed and the rotation starts in the clockwise direction p. Therefore, both the crankshaft eccentric 128 and the cam member 182 rotate in the same direction with the same maximum lateral displacement in opposite directions of the axis 186 occurring 90° past top dead center. (See Figure 12). The displacement angle θ at the end of the cam part phase 82 is related to each rotation radius R, , R, and the following equation holds true.

one θ=−− R.

Here, R1 represents the axis 188 of the crankshaft 82 and the eccentric portion l;
The radius R between the cam member 182 and the axis 186 of the cam member 182 is
is the radius between axis #184 of and axis 186 of eccentricity m128. Therefore, fc is greater than 0 (zero) and R1
is smaller than R2 (because the axis 186 of the eccentric portion 128 cannot actually be positioned on the periphery of the cam member 132,
It will definitely turn out like this. ), the cam 132 is 180°
Rotate by an angle smaller than . In order to maintain the lateral loads on the piston 94, and therefore to maintain friction losses at a reasonable level, R7 must be at least 1.
75R.

It is believed that it is desirable to choose equal to or greater than .

Figures 1 and 4 show the piston displacement ratio (percentage) and the crankshaft angular displacement (degrees) for various drive connection systems.
These are seven graphs plotted as a function of . As can be seen from the figure, the piston is 75% of the maximum displacement (1
00% corresponds to top dead center) or beyond (which is directly proportional to the angle of rotation of the crankshaft), the time required for the displacement to reach or exceed the normal connecting rod drive mechanism is relatively short. The connecting rod mechanism is much larger and has a longer length than the Scotchoke mechanism (SYM).
is actually much larger than would be the case due to simple string motion. Therefore, if the cam drive device shown in the figure is used, the line of motion of the piston will be overflowed, and the maximum dimension of the 7'C compressor and head should not be larger than the diameter of the motor stator. This significantly increases the time available for expelling discharged gas from the compression chamber while still allowing the use of shells.

To lubricate the electric motor tovf, an oil sump 140 is provided at the bottom of the lower shell portion 22, into which the conical end of the oil removal tube 1142 projects. The upper end portion of the oil outlet pipe 142 is cylindrical, and is relative to the lower end of the crankshaft 82. l! It is installed so that it cannot be turned once. As is well known to those skilled in the art, the centrifugal force imparted to the lubricant within the oil outlet tube 142 due to the rotation of the oil outlet tube 142 causes the lubricating oil to be biased toward the crankshaft 82 in the radial direction. The entire oil passage 144 provided inside is pumped out. Oil passage 144 extending in the axial direction
Lubricating oil is conducted to the main bearing 80 and to the bearing surface between the crankshaft eccentric 128 and the cam member 132 by radially outwardly extending passageways 146 and 148, respectively, in communication with the main bearing 80. It will be destroyed. Cam member 1
A pair of circumferentially spaced passageways 15 as shown in FIG. 4 to lubricate the interface between piston 82 and piston 94
0 and 152 are formed outwardly in the cam member 182.

In particular, an exhaust passage 1 extends radially inward from the outer surface of the crankshaft eccentric 128 in order to supply a suitable amount of lubricating oil to the upper bearing surface of the cam.
54t-, from the upper end of the cam member 182, apply a slight force 1 to 4 downward.
It is provided so as to communicate with the core passage 144 in a direction that crosses one end of the oil passage 144 in the direction 11Ia. 1st, 15th
As shown in the figure, a notch groove 156t is provided on the upper edge of the bearing surface with the cam member 1B2.
6 is disposed around the movement axis of the piston 94 on the non-load side of the bearing surface (that is, on the opposite side of the cylinder hole 72) over a range of approximately 1800 degrees in the circumferential direction. Therefore, when the crankshaft 82 rotates the eccentric i12.8, the passage 154 periodically communicates with the cutout groove 156, as shown in FIG. During this period, exhaust is performed from the oil passage 144 to the crankcase. This rotary pulping action subjects the upper end of the axial oil passage 144 to a relatively low pressure, thereby promoting the flow of lubricating oil through the oil passage 144. Since the exhaust passage 154 runs in a direction transverse to the axis of rotation of the crankshaft, lubricating oil is unlikely to be sucked into the crankcase during normal operation.

The compressor housing is configured to prevent lubricating oil from building up in the crankcase due to leakage from the bearings and/or suction through the exhaust passage 154, and to prevent excess pressure from building up within the crankcase. A lubricating oil return port 158 is provided in the flange vA60 on the lower side of the main pod 56. Preferably, a relatively small notch or recess 160' is provided surrounding the crankcase side of the return port 158 to provide collection and storage of lubricating oil.

A plastic tube 162 is provided extending downwardly from the lubricant return port 158 to minimize mixing of the lubricant with suction gas while returning to the sump 140. This tube 162 has a lower end portion of the limb tube 162 leaning against the outer shell portion 20 and a lower end portion of the tube 162 that is open at the lower end of the tube 162 and one of the spaces 122 between the motor stator 16 and the outer shell portion 22. It is slightly bent so that it can be positioned straight. The lower end of the tube 162 is cut at an angle to allow the return lubricating oil to be discharged toward the shell portion 20 and away from the suction gas, as shown.

The lubricating oil return port 158 and tube 162 have the smallest diameter within limits that allow the required oil flow and thereby reduce the pressure differential between the sift flank and the lower portion within the shell 12. It is desirable that the Encased pipe 16
2 is preferably relatively thick in length compared to diameter so as to impart relatively high dynamic ejection resistance.

This release 13IJ also includes a unique and novel assembly method that allows the various components to be quickly and easily assembled to form a compact and efficient electric compressor. Referring to No. 18N, the first step of assembling the electric compressor 10't'' is to assemble the compressor body 56 and the main bearing 8.
This is to perform finishing processing with respect to the outer diameter of 0. Once this is completed, the main bearing 80 is compressed into the hole 78 of the main pod 56, which is the compressor housing. The inner diameter of the bearing 80 is then machined to full final tolerances and the bearing surfaces provided within the bearing 80 are positioned concentrically with the compressor housing 56.

Next, the piston 94 is inserted into the cylinder hole 72 through the relatively large diameter hole 74 in the compressor housing 56, and then the crankshaft 82 and the cam side 182 are connected to the counterweight 9.
0 to the respective holes 88 and 106.
t-through and into the compressor no-crank and into the rond part of the piston 94.

The next step is to assemble the valve plate assembly 108 and head 110 to the compressor housing 56. For this assembly, and to ensure minimal re-expansion volume between the piston 94 and the valve plate assembly 108, the piston 94 is slightly offset from the housing face 164, as shown in FIG. It is first necessary to advance the piston 94 to top dead center, where it will protrude by a distance P. Next, measure the distance P'f'' between the top of the piston 94 and the valve plate 108. to the desired preset gap (typically on the order of 0.00 inches - about 1.5-1) to be provided. This sum is the required thickness G of the gasket 166 located between the crank 56 and the valve plate 108.
t-give.

Next, the diameter Ak of the housing 56 is measured by applying oil in a straight line transverse to the direction of movement of the piston 94.

Also, measure the maximum width B of the housing 56 at the same time as the movement of the piston 94.
Thickness G1 of valve plate 10) Thickness C of 8 and maximum thickness Dt-1 of head llO Add 0 This total CG 1 B+C+D-
) fi” then subtracted from the diameter A measured as above. Tight tightening is necessary to ensure operation of the piston 9.
Preferably, the overall dimension of the compressor assembly 14 in the direction of motion of 4 is slightly larger than diameter A. This is the intended gap value (typically 0.00 inches - about 1.5 inches)
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 is selected, the top of the housing 56 is then removed by first inserting a suction reed valve pin and a locating pin (not shown) into the appropriate openings provided in the housing 560 and 164. The valve plate device will be installed on the Next, the preselected valve plate gasket 166e is placed on the housing 56 positioned by the positioning pin, and the suction lead and valve plate 108 are subsequently placed on it. The discharge valve pin, discharge valve and backing (not shown) are then attached to the valve plate 1.
08 and pre-selected head gasgut 16.
8vi-Subsequently put on. The head 110 is then placed onto the housing 56 and the resulting assembly is clamped together and press fit into the upper shell portion 20.

As shown in FIG. 19, the motor stator 16e is press-fitted into the lower outer shell portion 422 of the motor stator 16e. In order to accurately position the crankshaft 82 in a concentric relationship with the center hole 126 of the motor stator 16, the stator 16 and the crankshaft 82 are
A mandrel 170' for positioning is inserted into the hole in between. Crankshaft 82? A small gap may be provided over all or part of the periphery of the lower shell portion 20.22 and between the flanges 24.26 to allow full adjustment for proper alignment. Next, temporarily weld the flanges 24° and 26 in the 2nd position facing each other, and then check the orientation of the assembly.
Change only 900, weld the tack again on the opposing 2nd place, and position the assembly? to bound.

The entire periphery of the flanges 24, 26 is then welded.

The thrust washer 172 and the holder 174 for the washer 172 (hereinafter 1, FIG. 1) are assembled to the crankshaft 82, and then the motor rotor 18 is attached to the crankshaft 82.
Heat shrink and fit. Connect the oil outlet pipe 142 to the crankshaft 8
2, and then the bottom portion 28 is welded and fixed to the lower end of the lower outer shell portion 22.

Next, a pair of annular gaskets 176 and 178"e shown in FIG. The lower member 44 is secured to the flange portion 58 by a plurality of bolts 54. The baffle member 48 is then secured to the assembly using the oak 180', and then the upper member 34 of the muffler 32 is assembled and attached. At the same time, weld the lower muffler member 84.44' to the north end of the upper outer shell portion 20, and simultaneously weld both members 84.44.
Also welds. The central portions of both members 84, 44 of the discharge muffler 32 are also welded together to complete the assembly.

The resulting compressor is a hermetic electric compressor that is extremely compact and easy to assemble; Only eight separate fasteners are required.

Figures 21 and 22 show an embodiment in which another mechanism is provided to assist in pumping to circulate lubricating oil to the bearing. In this embodiment, the crushing axis 8
an axial oil passage 1 similar to the one described above provided in 2;
A second passage 182k with a smaller diameter communicates with the upper end of the oil passage 144 on the radially inner end side of the oil passage 144 and extends in the axial direction.
, is formed in the crankshaft 82, and this second passage 1
Reference numeral 82 denotes an oil passage 144t which opens toward the upper end of the crankshaft 82 so as to constantly communicate with the inside of the crankcase. In order to maintain the pressure in the crank chamber at the suction pressure in the motor installation space or lower pressure, a pair of openings 184 and 186' are provided in the lower flange portion 60 of the housing 54.
A pressure-responsive reed valve 188 is attached to the openings 184 and 186, which overlaps the openings 184 and 186 and is attached to the flange portion 60 at one end. Therefore, as the piston 94 moves back into the crankcase during the suction process, the pressure increasing within the crankcase is absorbed by the opening 1.
84°186 is completely passed through and escaped. Then piston 9
4 moves away from the crankcase during the compression process, valve 188 closes and the pressure within the crankcase decreases. Oil such as leakage oil in the crankcase should be removed from the opening 18 marked L.
4, 186', and therefore the returned oil is returned to the space 122 between the outer shell portion 22 and the motor stator 16.
A baffle pipe 190 is provided which is guided to the oil sump 140, thereby preventing mixing of lubricating oil and suction gas. Opening 184
, 186 are preferably relatively large to provide sufficient opening cross-sectional area for exhaust (pressure relief) from within the crankcase, such exhaust being provided by the pressure relief valve of the discharge muffler. N is required when opening and discharging the discharged gas into the crankcase.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing an example of a hermetic electric compressor according to the present invention. FIG. 2 is a cross-sectional view taken along line 2-2 in FIG. 1. FIG. 3 is a cross-sectional view taken along line 3--3 in FIG. FIG. 4 is a cross-sectional view taken along line 4--4 in FIG. FIG. 5 is a perspective view of the piston used in the electric wire 1a shown in FIG. 1. FIG. 6, FIG. 7, FIG. 8, FIG. 9, FIG. 1O. 11, 12, and 13 are schematic cross-sectional views sequentially illustrating the operation of the drive device provided in the hermetic electric compressor shown in FIG. 1, respectively. FIG. L4 is a graph showing the displacement rate of the piston as a function of the displacement angle of the crankshaft for the drive used in the present invention and the other drive device. FIG. 15 is a cross-sectional view showing the upper end of the crankshaft in the electric compressor shown in FIG.
Along line 15. FIG. 16 is a graph showing the pressure fluctuations resulting from the reciprocating movement of the piston in the crankcase of the electric compressor shown in FIG. How to choose a head gasket in some exploded perspective views? It is illustrated. FIG. 18 is an exploded longitudinal sectional view of a portion of the compressor assembly shown in FIG. 1, illustrating the entire method of assembling the upper portion of the compressor assembly. FIG. 19 is an exploded longitudinal sectional view of the electric compressor shown in FIG. 1, illustrating a method of assembling the upper and lower parts of the compressor. FIG. 20 is an exploded longitudinal sectional view of a part of the electric compressor shown in FIG. 1, illustrating the entire method of assembling the discharge muffler provided in the compressor. FIG. 21 is a vertical sectional view of the other side of the electric compressor according to the present invention, showing the other side of the pressure relief mechanism from within the crankcase. FIG. 22 is an enlarged partial cross-sectional view of the pressure relief mechanism shown in FIG. 21, with the cross section taken at line 22--22 in FIG. lO... Hermetic electric compressor, 12... Outer shell, 14.
...Compressor assembly, 16...Morph stator, 18...
・Motor rotor, 20.22...Cylindrical outer shell part, 2
4゜26...7 rank part, 28...bottom part, 32.
...Discharge muffler, 84 ... Annular member, 44 ... Lower part member, 46 ... Sound deadening cavity, 4'8 ... Baffle fA
May, 54...Holt, 56...Main body (compressor housing), 58.60...7 Rank WIJ, 6
2 e 64...Side wall, 66...Cylinder wall, 72
... Cylinder hole, 74 ... Large diameter hole, 76 ... Suspension part, 80 ... Bearing, 82 ... Crankshaft, 9
0... Counterweight, 94... Piston, 96.9
8... Side wall portion, 104... Band-shaped portion, 106... Journal hole, -108°°° valve plate assembly, llo...
Head, ll'4128... Eccentric part, 180... Eccentric hole, 182 River force member, 134 River force member axis line, 18
6... Eccentric axis line, 138... Crank axis line, 1
40...Oil sump, 142...Oil extraction pipe, 144.
... Oil passage, 154 ... Exhaust passage, 156 ... Notch groove, 158 ... Lubricating oil return port, 162 ... Pipe, 1
66...gasket, 168°°° gasket, 17
0... Core metal, 182... Passage, 184.186...
・Opening, 188...Pressure responsive reed valve, 190...
baffle tube. -Koshi===J-7- -Two points=Stem==#=3. Yu6゜2=hai=mo;eni. Continuing from page 1 Priority claim @ July 25, 1983 ■ United States (US) [
] 516774 @ July 25, 1983 ■ United States (US) ■ 516904 o Inventor Earl Burnell Muir 14195 Charm Hill Drive, Sitney, Ohio, United States of America 45365 0 Inventor Walter Thomas Glasbaufte 5359 State Route 29, Sitney, OH 45365, United States

Claims (1)

[Scope of Claims] 1. A reciprocating compressor, comprising: A. a body forming a cylinder; B. a piston disposed to be able to reciprocate in the cylinder, including a head end portion and the head end portion; A piston that extends outward from the part and has a hole that penetrates through the piston, and c, J: a cam that is disposed in the great circle of the piston and that penetrates through the piston. a cam having an eccentric hole; a crankshaft driven by D6 rotation; the eccentric part of the crankshaft, in which the cam is disposed in the eccentric hole of the above-mentioned cam as shown in FIG. J:, the cam and the eccentric part of the crankshaft have the above 1 piston t-ζ1. during one cycle of the EE#i machine. The piston remains near top dead center for a longer period of time than the piston remains near bottom dead center! A reciprocating compressor configured to be driven as required. 26% ice range The reciprocating compressor according to claim 1, wherein the cam is rotatable about a first axis and the crankshaft is rotatable about a second axis,
The eccentric portion of the crankshaft and the curm are such that the second axis always lies between the head end portion of the piston and the first axis.
A reciprocating compressor is arranged so that it is located between the axis of the compressor. 8.% Allowance The reciprocating compressor according to claim 1 or 2, wherein the reciprocating compressor is configured such that the cam vibrates in an angular range as small as 18 (PJ). Machine. 4. Reciprocating machine 9 according to claim 2 or 8.
In the type compressor, the axis of the eccentric portion of the crankshaft is located at a distance mR1 from the second axis and at a distance from the first axis, and A reciprocating compressor that is set at the distance R1 shown or greater than the distance R1. 5. A reciprocating compressor according to claim 4, wherein the distance R is greater than 0 and the distance R7 is smaller than the radius of the cam. . 6. A reciprocating compressor according to claim 4 or 5, wherein the sine value of the maximum displacement angle of the cam is
A reciprocating compressor that is set to be equal to the ratio R1/R2 of the distances R, , R, described above. 7. A reciprocating compressor according to claim 4, 6 or 6, wherein the distance R, IRtkXR
Set it so that the following relationship holds: xkil, 75R+. Temeru reciprocating compression a. 8. The reciprocating compressor according to claim 6 or 7, wherein the reciprocating compressor is configured such that the maximum displacement amount of the piston is equal to the distance R302 times (2R,). Reciprocating compressor. 9. A reciprocating compressor according to any one of claims 1 to 8, wherein the head end portion and the connecting portion of the piston are formed integrally with each other. A reciprocating compressor. io, @ Claims 1. The reciprocating compressor according to any one of claims 1 to 9, wherein the connecting portion of the piston cooperates with a part of the body to generate a histone. A reciprocating compressor that includes a guiding surface that restricts the displacement of a piston across a reciprocating radius. 11. The reciprocating compressor according to claim 10, wherein the guiding surface tIII is provided on the piston on the opposite side of the head end portion. 12. A reciprocating compressor according to any one of claims 81 to 11, comprising an outer shell and an electric motor that drives the crankshaft vI, and A compressor assembly including a body, a piston, a cam, and a crankshaft is supported within the shell and the electric motor is disposed within the shell and distanced from the compressor assembly. A reciprocating compressor, the reciprocating compressor including a motor stator mounted on the compressor assembly, the motor stator being independent of the compressor assembly and supported on the shell. 1B, a reciprocating compressor according to claim 12, further comprising a cylinder head, the outer shell being the only means for positionally restraining the cylinder head on the body. Gold-biased reciprocating compressor. 14. &! in claim 12 or 18. A reciprocating BE assembling machine according to the invention, wherein the outer shells are fixed to each other and
A reciprocating compressor comprising a NJJl section and a second section, wherein the compressor assembly is supported only by the first section and the motor stator is supported only by the second section. 15.Claim 12, 13 or 14
The reciprocating compressor according to item 1, wherein the electric machine includes a motor rotor provided in the motor stator and supported by a 1ifJ compression horizontal compression body. io, @if in the 14th or 15th term of permission request
1 reciprocating compressor, the reciprocating compressor being press fit into the compressor assembly or the outer shell. 17. The reciprocating compressor according to claim 12, wherein the body, the cylinder head of the cylinder, and the valve assembly are in frictional engagement within the outer shell with the side of the outer shell. The reciprocating shell is supported solely by the podium and the shell constitutes the only means for mooring in the assembled configuration to the cylinder head and valve assembly described above. Compressor. 18. The reciprocating compressor according to claim 17, wherein the compressor assembly is formed into a substantially circular cross-sectional shape, and the compressor assembly has a substantially circular cross-sectional shape, and the compressor assembly 19. The reciprocating compressor according to claim 17 or 18, wherein the compressor assembly is fixed to a side wall of an outer shell. 201. A reciprocating compressor according to claim 12, wherein the reciprocating compressor has a diameter substantially equal to the diameter of A reciprocating compressor, which is equipped with a discharge muffler in which the fastener described in 1. is the only fastener used in the compressor. 2. Claims 12 to 19 The reciprocating pressure #I machine according to any one of claims, wherein the reciprocating compressor is provided with a discharge Lf-1 muffler forming one end wall of the outer shell. 2. Claim 21 The reciprocating Narita m machine according to the present invention, wherein the discharge muffler force; 1 plate member; and a ring-shaped second plate member having annular inner and outer convex circumferential edges superimposed and fixed to the inner and outer convex circumferential edges of the first grate member. a second grate member forming an annular sound-absorbing cavity with the fill material; The periphery...] is fixed to one end of the outer shell 1
, one end of the outer shell? A reciprocating compressor according to claim 21 or 22, wherein the reciprocating compressor has a closure 1 and a reciprocating compressor according to claim 21 or 22, wherein the discharge muffler is provided with an inlet for discharge gas,
A reciprocating compressor in which a porous member is provided overlapping the inlet. 2. A reciprocating compressor according to claim 23, wherein the porous portion is ? 1. A reciprocating type 2 having a U-shaped cross-sectional shape and arranged so as to occupy a circular portion within the sound deadening cavity, any one of claims 1 to 11 1. 1. The reciprocating compressor according to 1. , l: a reciprocating type in which the motor rotor is spaced apart from the motor stator so as to be driven by the motor stator and is supported only by the compressor; The reciprocating compressor described above is provided with an outer shell that surrounds the compression loss and has an oil reservoir for a lubricating oil phase in the lower part and an inlet for suction gas in the side wall. A housing defining a substantially closed crankcase is provided inside the housing, and a passageway including an exhaust port opening into the crankcase is provided for guiding lubricating oil from the oil sump to the compressor. , a reciprocating compressor according to claim 26, wherein the passage is provided within the crankshaft and overflows in the axial direction of the crankshaft. A reciprocating pressure m iso. 2. A reciprocating compressor according to claim 26 or 27, in which the exhaust port is selectively connected to the crankcase when the crankcase reaches a minimum pressure due to the reciprocating movement of the piston. and valve means for communicating the exhaust port into the crankcase, the valve means communicating the exhaust port into the crankcase to facilitate the flow of lubricating oil directed through the passageway to the compressor. Reciprocating - Compressor. 2. The reciprocating compressor according to claim 26 or 27 is provided with an opening that communicates between the inside of the crankcase and the inside of the outer shell, and the opening is provided with an opening that communicates with the inside of the crankcase. A reciprocating compressor equipped with a pressure-responsive valve that fully opens the opening when the pressure inside the outer shell is small. 30. An outer shell, a compressor housing defining a cylinder, a piston reciprocably disposed in the cylinder, a cylinder head, a valve assembly, and the above piston. 1. A method for assembling a hermetically sealed reciprocating electric compressor comprising a crankshaft, a motor for driving the crankshaft, which is associated with a motor stator and a motor rotor, and (a) ), assembling the above-mentioned piston and crankshaft into the above-mentioned compressor housing, and (b), J:, assembling the above-mentioned valve assembly and cylinder head on the above-mentioned compressor housing and overlapping with the above-mentioned cylinder. a step of assembling them in a matched arrangement to form a compressor assembly;
a step of press-fitting the valve assembly and the cylinder head so as to be positionally restrained between the compressor housing and the outer shell; 81. A method for assembling a reciprocating compressor as set forth in claim 80, comprising: a step of press-fitting the reciprocating compressor into the reciprocating compressor; The outer shell part
Separating from each other and forming each separately, the above-mentioned step (a),
An assembly method in which (b), (c) = (d) is performed in a state where the outer shell parts and the other shell parts are separated, and then both the outer shell parts are connected and fixed to each other. 82, a compressor assembly fixedly supported within a first shell portion, a motor stator fixedly supported within a second shell portion, and a closed type reciprocating electric motor. A method for assembling a compressor, the method comprising: (a) placing the outer shell portion of description 2 on a mandrel having a portion that tightly fits into a rotor receiving hole in the motor stator; (b), J:, &!, the first outer shell portion equipped with a crankshaft in the compressor assembly, the first outer shell portion protruding outwardly from one end of the first outer shell portion; positioning the first outer shell portion so that one end of the first outer shell portion is aligned with one end of the outer shell portion described in 2; the first and second outer shell portions are arranged in an assembled manner, and are precisely positioned concentrically with the crankshaft metal and the rotor receiving hole in the motor stator using the mandrel; (d) The above-mentioned first and second outer shell portions are mutually held at one end at each of the above-mentioned positions at multiple locations up to 1 with the relative position to the rotor receiving hole of the above-mentioned crankshaft kept constant. The tacking process includes a step of welding, and (e) a step of welding the above-mentioned first and second outer shell portions to each other at one end in an airtight manner over the entire circumference. How to assemble a type compressor. 88.% Allowance The method for assembling a reciprocating compressor according to claim 82, further comprising a step t1 of removing the mandrel and assembling a motor rotor to the crankshaft. 84. A method for assembling a reciprocating compressor according to claim 82 or 88, wherein seven runs 9 are installed in advance at each one end of the first and second outer shell portions.
In the steps (d) and (e), the first part is formed.
and an assembly method for completely preventing thermal distortion of the outer shell portion by welding the second outer shell portion to each other using these 7 runs and 9 parts. 85, % Claims 32, 3B or 84
2. The method for assembling a reciprocating compressor according to item 1, wherein in the step (d), the first and second outer shell portions are simultaneously temporarily assembled into two portions that are located opposite to each other when viewed in the diametrical direction. Assembly method using stop welding. 86. A method for assembling a reciprocating compressor according to claim 35, wherein in step (d), the above-mentioned first and second outer shell parts are mutually connected to the above-mentioned first temporary Tight welding is an assembly method in which two parts are temporarily welded with a phase difference of approximately 90°.