JPH0112952B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a scroll compressor that uses a combination of a fixed scroll and an oscillating scroll. [Prior Art] Prior to a detailed explanation of the present invention, the structure and operation of a scroll compressor using a scroll formed by connecting semicircular arcs will be briefly described. FIG. 1 shows a scroll formed by sequentially connecting semicircular arcs. That is, in FIG. 1, the scroll 1 draws a semicircle with radius (a-t)/2 and (a+t)/2 centering on point O, and then draws a semicircle a/2 apart from point O. point
Radius (2a−
Draw each semicircle of t)/2 and (2a+t)/2,
Thereafter, this process is repeated, and in the example shown in FIG. 1, four semicircular arc groups of basic pitch a and tooth thickness t are successively connected in a scroll shape. Hereinafter, such a configuration will be referred to as a two-turn scroll.
Note that the end of the smallest semicircular arc of this scroll 1 is placed in a semicircular arc whose diameter is the tooth thickness t. Further, FIG. 2 shows the principle of operation of a scroll compressor constructed by combining one set of scrolls shown in FIG. 1, and in this FIG. 2, 2 is a fixed scroll; 3 is an oscillating scroll that is symmetrically combined with the fixed scroll 2 . Here, the fixed scroll 2 is stationary and fixed at the arrangement position, and its center O ₁ corresponding to the point O is immovable . Due to the combined arrangement, there is a space between the fixed scroll 2 and the
Compression chambers 4 and 5 consisting of closed circular arc spaces
is formed. Then, the center O ₂ of the oscillating scroll 3 with respect to the point O' is set at O 2 - around the fixed point A corresponding to the point O' of the fixed scroll ₂ .
If the distance of A is maintained at a/2-t and it is rotated, that is, oscillated or revolved without changing its attitude, the angles of 0°, 90°, 180°, and 270° are shown in Fig. 2. As shown in the angular position, the compression chambers 4, 5 are
Once opened at the outer periphery, the volume is gradually reduced toward the center, and if the object to be compressed is a fluid, the fluid can be taken out from the discharge port 31 shown by the dotted line. Note that during this operation, point B at the center of the outer end of the scroll of the swinging scroll 3
is between the fixed point A and the center of the fixed scroll 2 .
Around the fixed point C on the line D-D' connecting _O1 ,
A circular motion of radius a/2-t will be performed. In this way, a compressor can be constructed by symmetrically combining one set of scrolls. By the way, as for this type of scroll compressor, US Pat. The crankshaft is supported in the radial direction by a rolling bearing provided in the main body at a position surrounding the eccentric hole, and the lower surface of the oscillating scroll base plate is connected to the rolling bearing of the main body at a position surrounding the eccentric hole. It is supported in the thrust direction at a peripheral portion radially outward from the bearing. In this configuration, the crankshaft is supported in the radial direction by the main body via the rolling bearing at the position surrounding the eccentric hole of the crankshaft, so the radial force generated on the oscillating scroll is primarily absorbed by the eccentric hole. The first and second points of action are close to each other in the axial direction, so the moment generated on the crankshaft is small, and as a result, the moment on the crankshaft is Prying is prevented. However, a balancer is provided in the radial direction on the end face of the crankshaft where the eccentric hole is provided to balance the swinging scroll, and this balancer can be rotated between the base plate of the swinging scroll and the main body. In order to achieve this, the support surface of the main body that supports the oscillating scroll in the thrust direction is provided on the outer periphery in the radial direction from the balancer. As a result, the oscillating scroll base plate is supported at its outer edge, and as is clear from the operating principle of the scroll, the center side of the oscillating scroll, which is the high pressure side, is not supported in the thrust direction.
The base plate deforms in the axial direction due to the gas load, and the oscillating scroll shaft formed perpendicular to the base plate also collapses due to the deformation of the base plate, causing twisting in the thrust bearing and eccentric hole, and effective lubrication cannot be performed. This caused problems with bearing reliability. [Summary of the Invention] The present invention has a flange portion of the main body that supports a crankshaft in the radial direction on a protrusion of the main body, and a shaft hole surrounding an eccentric hole into which an oscillating scroll shaft of the crankshaft is fitted. Thrust bearings for supporting the rocking scroll base plate in the thrust direction are integrally formed on the peripheral edge of the shaft hole, and an oil passage provided in the crankshaft, a sliding surface between the shaft hole and the crankshaft, The above-mentioned drawbacks are eliminated by supplying lubricating oil to the peripheral edge of the shaft hole that supports the base plate in the thrust direction through the sliding surfaces of the oscillating scroll shaft and the eccentric hole. This was done as intended. [Embodiments of the Invention] Examples of the scroll compressor of the present invention will be described. 3 to 6 show an embodiment of the above-mentioned swinging scroll 3 , and FIGS. 7 and 8 show an embodiment of the support and swing mechanism for the swinging scroll 3 . It shows. In FIGS. 3 to 6, the swinging scroll 3 has swinging scroll teeth 6, a swinging scroll base plate 7 with the swinging scroll teeth 6 protruding from one surface, and a swinging scroll base plate 7 having the swinging scroll teeth 6 protruding from one surface. An oscillating scroll shaft 8 extending on the surface, and oscillating guide recesses 9 similarly formed on the other surface at equal angular intervals on a concentric circle;
It consists of an oscillating scroll balancer 10,
The reference numeral 11 is a virtual extension line of the inner surface of the swinging scroll tooth 6. In addition, in FIGS. 7 and 8, each guide pin 12 having a shaft end with a smaller diameter loosely fitted into the swing guide recess 9 of the swing side scroll 3 is connected to a flange portion of the main body 13 . The oscillating scroll base plate is supported by each guide pin hole 14 formed in 13a corresponding to each of the recesses 9, and is also supported by a thrust bearing surface (sliding surface) 15 provided at the peripheral edge of the shaft hole 16, which will be described later. 7 is in contact with the shaft hole 16 which is bored in the protrusion 13b at the center of the main body 13 on both sides thereof.
The oscillating scroll shaft 8 is pivotally supported in an eccentric hole 18 of a crankshaft 17 rotatably supported.
Therefore, when the crankshaft rotates, a sliding surface 24 is formed between the inner circumferential surface of the shaft hole 16 and the outer circumferential surface of the crankshaft 17.
is formed. 19 is an oil hole (oil passage) passing through the center J of the crankshaft 17 and communicating its end with the eccentric hole 18; 20 and 21 are a plurality of radial holes communicating between the oil hole 19 and the sliding surface 24; The oil holes are formed on the end side of the protrusion 13b so as to be spaced apart from each other in the axial direction. 22 is an oil groove provided on the thrust bearing surface 15, and 23 is an oil groove provided on the inner surface of the eccentric hole 18. Therefore, according to the embodiments shown in FIGS. 3 to 8, the swing scroll shaft 8 of the swing scroll shaft 8 is connected to the eccentric hole 18 of the crankshaft 17 , and each swing guide recess 9 is connected to each guide pin 12. As the crankshaft 17 rotates from 0° → 90° → 180° → 270° as shown in FIG. 9, the oscillating scroll 3 rotates as shown in FIG. Then, the relative position remains the same and the swing is performed. However, when the lever swings, the distance between the center J of the crankshaft 17 and the center K of the swinging scroll shaft 8 needs to be maintained at a/2-t as explained in FIG. In order to make it happen, the 9th
As shown in the figure, if the diameter of the guide pin 12 is b, then the diameter of the swing guide recess 9 must be a+b-2t. Furthermore, in FIGS. 3 and 5, E~
E', F to F' and G to G' are each a base line, K is the center of the oscillating scroll shaft, h is the height of the oscillating scroll tooth, and I is the position of the center of gravity of the oscillating scroll tooth portion when there is no balancer. That is, in this way, a predetermined swing trajectory can be constructed by at least three swing guide recesses 9 and each guide pin 12 that is loosely engaged with the swing guide recesses 9. Now, regarding the balancing of the swinging scroll 3 according to the configurations of the embodiments shown in FIGS. 3 to 6, as is clear from the drawings, the center of gravity of only the swinging scroll teeth 6 is located at the base line G~ It will be located near point I on G'. This is due to the fact that the shape of the scroll teeth is not symmetrical. If this swinging side scroll 3 is replaced by a balancer 10
If the rocking motion is to be made as described above in a state where there is no This is because the swinging side scroll 3 performs a swinging motion, and in such a case, it is very difficult to achieve balancing. For this purpose, a balancer 10 is provided in the embodiment,
The center of gravity of these scroll teeth 6 and the balancer 10 is made to coincide with the center K of the oscillating scroll shaft, and in order not to impede the operation, it is placed outside the virtual extension line 11, It is sufficient to select a shape that has the same height as the scroll tooth height h and the center of gravity in the height direction, and also selects its mass, so that the entire center of gravity of the swinging side scroll 3 is the same as that of the swinging scroll. equal to the center K of the axis,
Moreover, balanced eccentric rotation can be performed around the center J of the crankshaft. The details of the crankshaft 17 are as follows.
As shown in the figures or FIG. 12, the base end of the shaft is stepped to form a motor mounting part 26, and an oil groove 27 is formed on the outer periphery of the shaft. Falling off from the shaft hole 16 is prevented. Therefore, the flange 28 and the shaft hole 16
Since the crankshaft 17 is rotatable using the joint surface with the flange 28 as a sliding surface, a space 25 is formed around the flange 28 as shown in FIG. Next, an embodiment of the fixed scroll 2 combined with the swinging scroll 3 is shown in FIGS. 13 and 14, and the position and size of its discharge port will be described in particular. In these FIGS. 13 and 14, the fixed scroll 2 has fixed scroll teeth 29,
The fixed scroll teeth 29 are replaced by the swinging scroll teeth 6.
It consists of a fixed scroll base plate 30 protruding from one surface corresponding to the above, and a discharge port 31 having the position, shape and size shown below is formed. Here, the fixed scroll teeth 29 have a tooth height h equal to that of the oscillating scroll teeth 6, and the discharge port 3
1 is eccentric from the center point by a distance c and has a diameter d. In this configuration of the fixed scroll 2 , as is clear from FIG. 2, the diameter d of the discharge port 31 is made smaller than at least the scroll tooth thickness t, and is large enough to seal the discharged fluid. In order to completely discharge the fluid in the compression chamber 4 (FIG. 2), its center must be on the base line N to N', and the point p on the inner circumference must be in contact with the innermost edge of the fixed scroll tooth 29. In other words, the requirements for the specifications of the discharge port 31 are as follows:
It is eccentric by (a/2-t≦c<a-t/2), and its center is on the base line N~N' that connects the center of the base plate and the innermost edge of the scroll tooth, and the point p on the inner circumference of the opening is Occupies a position adjacent to the innermost edge of the scroll teeth, and
It is nothing but a circular shape with a diameter d (d=a-t-2c or 0<d≦t). One embodiment of a scroll compression mechanism formed by assembling each of the above-mentioned components is shown in FIGS. 15 and 1.
As shown in FIG. 6, a cylinder 32 is disposed on the outer edge of the flange of the main body 13 , a suction port 33 is formed in the cylinder 32 to communicate with a suction space 34, and the fixed scroll 2 is aligned with the cylinder 32 . They are connected by bolts 36 through bolt holes 35, and this cylinder 32 also plays the role of adjusting and setting the axial height and distance between the fixed and swinging scrolls 2 and 3 . P-P′,
Q-Q' is the baseline. Further, FIG. 17 shows a scroll compressor of a closed type in which an electric motor is incorporated into the scroll compression mechanism constructed in this manner. FIG. 17 shows a scroll compressor according to an embodiment of the so-called high-pressure shell type in which the inside of the closed shell is maintained at the discharge side pressure.
In FIG. 7, the rotor 37 constituting the electric motor has an end ring 38 and a balance weight 39, as is clear from FIG. The above-mentioned scroll compression mechanism is attached to the mounting flange 43 provided around the upper inner side of the shell 42, which forms an induction motor and seals the whole, with its bolt 36, and the suction introduced through the shell 42. A pipe 44 is connected to the suction port 33, a discharge pipe 45 is taken out from the shell 42, and a communication port 4 is provided that connects the mounting flange 43 with the shell inner space 47.
6, and lubricating oil 48 is stored at the inner bottom of the shell. The lead wire 49 of the stator 40 is taken out to the outside of the shell through a hermetic terminal 50, and the stator 40 is fixed to the inner surface of the shell 42 through a gap 51, and the rotor 3
7 has a mounting hole 5 in the center thereof so as to be opposed to the stator 40 with an air gap 52 interposed therebetween.
3 is fixed to the mounting portion 26 of the crankshaft 17 by, for example, shrink fitting. Therefore, in the embodiment shown in FIG. 17, when the crankshaft 17 is driven to rotate by energizing the electric motor,
Through the shaft 8 rotatably fitted in the eccentric hole 18, the swinging scroll 3 is guided by the guide pin 12 whose recess 9 is loosely engaged, and the swinging motion shown in FIG. 2 is achieved. The gas flowing from the suction pipe 44 to the suction space 34 is sucked into the compression chamber 4,
5 to compress the shell internal space 47a from the discharge port 31.
It can be discharged to the outside through the discharge pipe 45. However, during the compression operation of the lever, the shell internal space 47b
The discharge gas flows through the communication port 46 to create a high-pressure atmosphere with a discharge pressure. Therefore, the shell internal space 47
Due to the discharge pressure acting on b, the lubricating oil 48 stored in the oil reservoir at the inner bottom of the shell is discharged from each oil passage 19, 20, 21 and oil groove 22, 23, 27 as shown by the single line arrow. It is supplied to each lubricating part, reducing loss due to wear on sliding surfaces. That is,
The oscillating scroll shaft 8 and the eccentric hole 1 are connected through the oil hole 19.
The lubricating oil that has reached the connection part with 8 and the lubricating oil that has reached the oil holes 20 and 21 from the oil hole 19 is transferred to the oil groove 23 and the sliding surface between the orbiting scroll shaft 8 and the eccentric hole 18 of the crankshaft 17. A sliding surface 24 between the oil groove 27 and the inner peripheral surface of the shaft hole 16 of the main body 13 and the outer peripheral surface of the crankshaft 17
In the process of reaching the pump, the pressure is reduced and the pressure in the space 25 becomes lower than that in the discharge, so the lubricating oil flows due to the differential pressure. Furthermore, the lubricating oil that has reached the space 25 is squeezed by the oil groove 22 and the crank bearing surface 7,
This leads to the lowest pressure suction space with some pressure loss. In addition, the above-mentioned differential pressure and oil hole 2 are connected to the sliding surface 24.
The lubricating oil is supplied by the centrifugal force acting on the lubricating oil in the oil holes 20 and 21, and the lubricating oil is sufficiently supplied to the sliding surface 24 between the oil holes 20 and 21. Therefore, the oil holes 20, 21
The sliding surface 24 between the edges is filled with lubricating oil to form an oil seal film, and the sliding surface 24 on the end side of the protrusion 13b is
Even if the high-pressure gas in the shell inner space 47b tries to enter from between, it is blocked. Furthermore, during operation, the pressure inside the compression chamber 4 near the discharge port 31 is highest, and a thrust force acts on the base plate 7 of the oscillating scroll 3, but the thrust bearing surface 1
5 is located near the base plate 7 of the oscillating scroll.
Since the base plate 7 is supported, the base plate 7 does not bend and operation can be performed smoothly. The lubricating oil is then transferred to the fixed and swinging scroll teeth 29, 6 along with the suction gas.
The air is discharged into the shell inner space 47a with a seal formed between the two, separated from the compressed gas, and returned to the shell inner bottom again. That is, the lubricating oil, the oil seal, and the oil separation function are performed by pumping using differential pressure in this manner. In particular, during the compression operation, the swing side scroll 3 has its base plate 7 and the thrust bearing surface 1 of the main body 13 due to the compression action in the compression chambers 4 and 5.
A thrust load is generated between the oil groove 22 and the oil groove 22.
The load can be reduced by applying oil pressure to the engine. The balance weight 39 balances the swinging scroll 3 that performs an eccentric movement around the rotation center J of the crankshaft 17. Further, as shown in FIG. 19, for pumping, a screen 55 is inserted into the oil hole 19 at the center of the shaft, and the lubricating oil is supplied by the pumping action accompanying the rotation of the shaft. In this case, the same effect as in the embodiment shown in FIG. 17 can be obtained. [Effects of the Invention] As described above, in the present invention, the shaft hole that supports the crankshaft in the radial direction relative to the protrusion of the main body and that surrounds the eccentric hole into which the oscillating scroll shaft of the crankshaft is fitted is provided in the main body. A thrust bearing for supporting the rocking scroll base plate in the thrust direction is integrally formed on the periphery of the shaft hole at the flange portion of the shaft hole, and an oil passage provided in the crankshaft is connected to the shaft hole and the crankshaft. The lubricating oil is supplied to the peripheral edge of the shaft hole that supports the base plate in the thrust direction through the sliding surface and the sliding surface between the oscillating scroll shaft and the eccentric hole. The bearing configuration is simplified, and since the thrust bearing is formed at the periphery of the shaft hole, it supports the high-pressure part of the compression chamber, preventing deflection of the oscillating scroll base plate, and also supporting the thrust bearing. The distance of the oil supply system can be shortened, and smooth lubrication can be performed without delay in oil supply at startup.

[Brief explanation of drawings]

Fig. 1 is an explanatory diagram of a scroll formed by sequentially connecting semicircular arcs with different radii in a scroll shape, Fig. 2 is an operational diagram of a scroll compression mechanism constructed by mutually combining a set of scrolls as described above, and Fig. 3 4 is a plan view and a bottom view of the swinging scroll, and FIGS. 5 and 6 are EE' and FH-
Each sectional view of the G' section, FIG. 7 is a longitudinally sectional front view of the main parts showing the support and swing mechanism of the swinging side scroll, FIG. 8 is a plan view of the same supporting part, and FIG. 9 is the swing mechanism. 10, 11 and 1
Figure 2 is a side, cross-sectional, and end view of the crankshaft, Figure 13 is a plan view of the stationary scroll, Figure 14 is a sectional view taken along line N-N' in Figure 13, and Figures 15 and 16 are scroll compression. FIG. 17 is a side cross-sectional view and a plane cross-sectional view of the P-P' and Q-Q' portions according to an embodiment of the mechanism; FIG. 17 is a vertical cross-sectional view showing a scroll compressor according to an embodiment of the high-pressure shell type; FIG.
The figure is a perspective view showing the electric motor rotor combined with the crankshaft, and FIG. 19 is a partial sectional view illustrating the oil supply system using the screw. 1 ...Scroll, 2 and 3 ...Fixed side and swing side scroll, 4, 5...Compression chamber, 6...
Oscillating scroll tooth, 7...Occillating scroll base plate,
8... Oscillating scroll shaft, 13 ... Main body, 13a
...Flange part, 13b...Protrusion part, 15...Thrust bearing surface (sliding surface), 16...Shaft hole, 17 ...
... Crankshaft, 18 ... Eccentric hole, 19 ... Oil hole (oil passage), 20, 21 ... Oil hole, 22, 23, 27
... Oil groove, 24 ... Sliding surface, 25 ... Space, 28
...Brim portion, 29...Fixed scroll tooth, 30...
Fixed scroll base plate, 31... Discharge port, 32...
Cylinder, 33... Suction port, 34... Suction space,
37...Rotor, 40...Stator, 42...Shell, 43...Mounting flange, 44...Suction pipe, 45...Discharge pipe, 46...Communication port, 47a,
47b...Space inside the shell, 48...Lubricating oil.

Claims (1)

[Claims] 1. A shell 42, a flange portion 13a installed in the shell 42, and a protruding portion 13b that protrudes downward from the center of the flange portion 13a and has a shaft hole 16 penetrating both the upper and lower sides. A main body 13 is integrally formed with the main body 13, and the main body 13 is rotatably inserted into the shaft hole 16 of the main body 13, supported in the radial direction, and surrounded by a portion corresponding to the root of the protrusion 13b on the upper end side. A crankshaft 17 having an eccentric hole 18, an oscillating scroll shaft 8 rotatably fitted into the eccentric hole 18 of the crankshaft 17, and a base plate supported in the thrust direction at the peripheral edge of the shaft hole 16 of the flange portion 13a. 7 and scroll-shaped teeth 6 and housed in the shell 42; a base plate 30 facing the base plate 7 on the opposite side from the main body 13; a fixed scroll 2 disposed within the shell 42 and having scroll-shaped teeth 29 that are combined with the teeth 6 of the scroll 3 to form compression chambers 4, 5;
An oil passage 19 for supplying lubrication is provided to penetrate the crankshaft 17 in the axial direction, and a sliding surface between the oil passage 19, the shaft hole 16 and the crankshaft 17, and the oscillating scroll shaft 8. The above eccentric hole 18
A scroll compressor characterized in that the scroll compressor is configured to be supplied to the periphery of the shaft hole 16 that supports the base plate 7 in the thrust direction through the sliding surfaces thereof. 2. The scroll compressor according to claim 1, wherein the crankshaft 17 is supported by the inner circumferential surface of the base of the main body protrusion 13b and the inner circumferential surface of the lower end of the protrusion 13b.