JPS58106190A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To reduce the starting torque, to prevent abrasion, and to improve the performance by making the revolution radius of a revolution scroll member against a stationary scroll member variable due to the autorotation of an eccentric bush caused by the eccentric rotation of a crank pin. CONSTITUTION:An eccentric bush 500 is rotatably sheathed around a crank pin 23 and is inserted in a radial needle bearing 26, and the outer diameter center is located at O' and the inner diameter center at O'', thus having the eccentricity of (e), and the center of gravity G is located at a distance (g) from the inner diameter center O'' on the opposite direction to the outer diameter center O'. Accordingly, the revolution radius (f) of a revolution scroll member 24 against a stationary scroll member (not shown in the diagram) is made variable due to the autorotation of the eccentric bush 500, thereby, for example, the rotating direction is restricted so as to increase the revolution radius (f) during the low speed rotation, thus offering excellent seal between both vortexes and a high efficiency operation.

Description

[Detailed description of the invention] The present invention relates to a scroll compressor.

As shown in the operating principle diagram in Figure 1, this type of compressor has two spiral bodies of the same shape, one of which 2 is fixed to a sealed end plate having a discharge port 4 approximately in the middle, and the other spiral body l is fixed to the other end plate, rotated both by 180° relative to each other as shown in Fig. 1, and the spiral bodies of both
．． 52, 51', and 52', the spiral bodies 2 are stacked on top of each other with a relative shift of a distance of 2ρ (= pitch of the spiral - 2 x thickness of the spiral), and one of the spiral bodies 2 is held stationary. Then, the other spiral body l is connected to one spiral body 2 by a crank mechanism having a crank radius ρ.
radius ρ = 00' without rotating around the center 00 of
It is configured so that it makes an orbital motion.

Then, two spiral bodies 1. A sealed small chamber 3°3 is formed between the points 51 and 52 where both the spiral bodies abut and between the points 51' and 52', and the volumes of the closed chambers 3 and 3 change as the spiral body l revolves. Gradual change 〇 In other words, the spiral body l is first turned to 90° from the state shown in (1) in the same figure.
When it revolves, it becomes (2) in the same figure, when it revolves 180 degrees, it becomes (3) in the same figure, and when it revolves 270 degrees, it becomes (4) in the same figure.During this period, the volume of the small chamber 3 gradually decreases, Figure (4)
In this case, the two small chambers 3 and 3 communicate with each other to form a small chamber 53, and when the state of FIG. 3), and the volume becomes the smallest between (3) and (4) in the same figure, and during this time, the outer space that began to open in (2) in the same figure becomes (3) in the same figure. , moving from figure (4) to figure (1),
New gas is taken in to form a closed chamber, which is then turned over, and the gas taken in from the space outside the spiral body is compressed and discharged through the discharge port 4.

The above is the operating principle of the scroll type compressor. Specifically, as shown in the longitudinal sectional view of FIG. 2, the scroll type compressor has a front end plate 11.
Rear end plate 12. When the intake port 14 and the discharge port 15 are protruded from the rear end plate 12, the cylinder plate 13 is fixed to the front end plate 11. crank pin 23
A third main shaft 17 is pivotally connected to the crank pin 23.
Radial needle bearing 2, as shown in Figure ■-■ cross section
6. Post 243 of the revolving scroll member 24. Square tube member 2
71. Sliding body 291° Ring member 2921 Stopper 29
A revolving scroll member 24 including a spiral body 242 and a disk 241 is attached via a revolving mechanism such as a third order.

However, such a scroll compressor has the following major drawbacks.

(1) As shown in FIG. 1 (1) to (4), the small chambers 3 and 3 sealed in 91 gradually decrease in volume as the revolving spiral body 1 revolves, and become small chambers 53. However, at this time, a region where the small chambers 3, 3 or the small chamber 53 do not communicate with the discharge port 4, that is, the rotation angle range is short, so that liquid (for example, lubricating oil) is added to the gas taken from the space outside the spiral body. When a certain amount of gas is mixed in, the gas is first compressed, and then the liquid is compressed. However, since the liquid is an incompressible liquid, when the spiral body rotates further, an abnormal pressure increase occurs, and this is normal. liquid compression), spiral body (Fig. 1 1, 2, Fig. 2 242゜25
2) may be damaged.

Furthermore, when the compressor is started, at least some liquid refrigerant or oil accumulates inside the compressor housing 10 and the small chamber (see Figure 1, 3, 53), so a large compressor starting torque is generated. For this reason, a large starting torque is required of the external motor, and when the compressor is mounted on a vehicle and driven by a driving engine, the engine load temporarily increases at startup, causing a so-called shock (compressor startup). (shock) occurs, which changes the driving feeling of the car.

(2) Also, if foreign matter such as dust enters the compressor and gets caught in the contact area between both spiral bodies, the spiral body may be damaged or scratched, which may cause normal compression. If you don't do it, you won't be able to do it.

(3) Also, as described above, the eccentricity ρ of the crank pin 23 from the main shaft 17 gives the radius of revolution, and 2ρ gives the offset i of both spiral bodies.

If the amount of eccentricity ρ is smaller than a predetermined dimension, the two spiral bodies will not come into contact with each other (the contact points at 51゜52.51' and 52' in Fig. 1 will disappear), and for this reason, gas will flow from the two spiral bodies. This can lead to leakage and a significant drop in the performance of the compressor.On the other hand, if the eccentricity ρ is large, both spiral bodies will come into strong contact with each other, requiring a large amount of power to rotate the compressor. There is a problem that the crank pin 23 is worn out, and extremely high precision machining is required to obtain the eccentricity ρ of the crank pin 23.

(4) Furthermore, in this type of compressor, as shown in Fig. 1 (1
), the volume of the small chambers 3 and 3 becomes the theoretical suction amount, and this theoretical suction amount, that is, the discharge amount, cannot be changed.
If the vehicle is used for refrigeration and is driven by the engine for driving, it generates more refrigeration capacity than necessary when driving at high speeds, and this places a large load on the engine for driving at steady speeds, resulting in a reduction in vehicle speed.

This results in deterioration of vehicle fuel efficiency, etc.

The present invention was proposed in view of these circumstances, and aims to reduce the starting torque without causing liquid compression, prevent damage, and
For the purpose of providing a variable displacement scroll compressor that improves performance and prevents wear, the center of the inner diameter and the center of the outer diameter are eccentrically defined as the center of the outer diameter with respect to the center of the inner diameter. An efficient link push having a center of gravity on the opposite side is rotatably inserted between the crank pin side of the main shaft and the revolving scroll member side via a spring, and the above mentioned efficient link push due to the eccentric rotation of the crank pin is The invention is characterized in that the revolution radius of the above-mentioned revolving scroll member relative to the stationary scroll member is made variable by the rotation of the push.

To explain the embodiment of the present invention with reference to the drawings, FIG. 4 is a cross-sectional view of the first embodiment showing its revolution mechanism, and FIG. 5 is a cross-sectional view of the first embodiment.
The vertical sectional view of the figure, Figures 6 (A) and (B) are respectively a partial enlarged view of Figure 5, its front view, and Figures 7 (1) to (4).
are respectively action explanatory views of FIG. 4, FIGS. 8 and 9 are front views showing a modification of FIG. 6, FIG. FIG. 2 is a partial vertical cross-sectional view of a revolution mechanism according to a second embodiment.

First, in the first embodiment shown in FIGS. 4 to 6, the same symbols as in FIGS. 2 to 3 indicate the same members as in FIGS. 2 to 3, respectively.
500 is rotatably inserted into the crank pin 23.
501 is an eccentric part of the efcentric push, 502 is an eccentric This is an unbalanced mass integrally attached to the part 501, so that, as shown in FIG. 503, which is the position g, is a coiled spring material that is inserted into the crank pin 23 and restricts the rotational direction of the Efcentric Push 500, and the circumferential position where the Efcentric Push 500 is stopped by the spring material 503. so that the direction connecting the center of the crank pin 23 and the center of the main shaft 17 is equal to the direction oo''.
The position is such that the revolution radius of the scroll member 24 is relatively large.

In Fig. 7, if 0 is the center of the main axis 17 and R is the distance between O and o'', then (1) in the same figure is
This shows the case where the outer diameter center O' and the inner diameter center 0'' are on the extension of the main axis center O and the inner diameter center O'', and in this case, the revolution radius OO' of the spiral body is the maximum, and this value ρmax is equal to ρmax = R+ e Next, (3) in the same figure shows the effect of efcentric push 500
The outer diameter center 0' of is above the main axis center O and the inner diameter center O'' of the Efcentric Push 500. In this case, the revolution radius OO' of the spiral body is the minimum, and this value ρmin is ρm1n= In other words, as shown in (4) of the same figure, the revolution radius ρ of the spiral body due to the efcentric push 500 is R-e.

When such a scroll type compressor is operated, the state approximately shown in Fig. 7 ('1) is maintained when the rotation speed of the compressor is relatively low. dripping In other words, at relatively low speed rotation,
When the main shaft 17 is rotated, the efcentric push 5
00 is restricted from moving in the rotational direction by the spring material 503, and thus at the revolution radius at the position where the two spiral bodies touch (for example, 51, 52, 51', 52' in Fig. 1). The compressor operates extremely well.

Here, when the rotational speed of the compressor is increased, centrifugal force is applied to the Efcentric Push 500 inserted into the crank bin 23, but the center of gravity G of the Efcent Link Push 500 is equal to the inner diameter of the Efcentric Push 500. Efcentric push 5 regarding O// shifted from center 0″
Since it is on the opposite side from the outer diameter center O' of 00, the state shifts from the state shown in FIG. 1 (1) to the state shown in FIG. The equilibrium position at that time is determined by the restoring force of the spring material 503 and the magnitude of the centrifugal force applied to the center of gravity G. If the rotation speed is high as described above, the F-centric push 500 will have a large centrifugal force. The revolution radius ρ of the compressor is increased until this point is balanced with the restoring force of the spring material 503.
Make smaller.

Therefore, when the compressor becomes faster, the e-centric push 500 rotates so that the revolution radius ρ of the compressor decreases, and as a result, until then, the
, 52', the closed chamber 3 was formed by the two spiral bodies 1 and 2 coming into contact with each other. 3. 53 is a spiral body 1. 2 are no longer in contact with each other, a gap is created between the two spiral bodies, and the fluid to be compressed leaks from the gap to the low pressure side, resulting in a decrease in the discharge amount of the compressor.

Moreover, even when the compressor rotates at low speed, the small chamber 3 shown in FIG.
3. 53 etc., for example, confine a liquid such as liquid refrigerant or oil and perform so-called liquid compression, the abnormal surface force will cause the swirling body 2
4, which is transmitted to the efficient link push 500 via the radial needle bearing 26.

At this time, the F-centric push 500 has a spring of 1
7 (2),
As shown in (3), it rotates so that the revolution radius ρ becomes smaller. Until then, Fig. 1 51.52.51
As shown in ', 52', the closed chamber 3゜3.53, which was formed by the two spiral bodies 1 and 2 coming into contact with each other, is no longer in contact with the spiral bodies 1 and 2, and a gap is created. In particular, the liquid will escape from this gap and the abnormal pressure rise will be eliminated.

In addition, if the two spiral bodies catch a foreign object such as dust, an abnormal force will be generated as well, so the E-centric push 500 rotates to reduce the orbital radius ρ and remove the foreign object from the shell. This results in continued good compressor operation.

According to such a device, the following effects can be achieved.

(1) When the rotational speed of the compressor is relatively low, the rotational direction of the Efcentric Push 500 is restricted by a spring so as to increase the revolution radius ρ, and this
The two spiral bodies are well sealed without any gaps, forming a closed chamber, resulting in extremely good operation.

On the other hand, when the rotational speed of the compressor increases, the centrifugal force applied to the efcentric push 500 causes the efcentric push 500 to rotate, reducing the orbital radius.
A gap occurs between the two spiral bodies, fluid leaks from this gap, and the discharge amount of the compressor decreases. As a result, both the compressor capacity (discharge amount) and the required power of the compressor greatly increase. descend.

(2) Even when the compressor rotates at low speed, if abnormal force is generated in the spiral body due to compressed liquid or foreign matter such as dust,
F-centric push 500 has crank pin 23
Because it rotates (rotates) and escapes with a small orbital radius ρ, liquid is released or foreign matter is left behind.
The major drawbacks of conventional systems, such as destruction of the spiral body and dull driving feeling caused by the large starting torque, can be overcome.

(3) In the conventional system, the revolution radius ρ is uniquely determined by the amount of offset between the spindle center and the crankbin center. However, in this device, the revolution radius ρ can vary within the range of R-e ≦ ρ ≦ R + e, so the offset amount R between the spindle center and the crank bin center can be processed with a certain level of accuracy. Good and extremely easy to work with.

Furthermore, the purpose of efcentric push is to
It is necessary to determine the center of gravity position of the Efcentric Push so that the revolution radius ρ is small during high-speed rotation.In other words, the Efcentric Push is placed on the opposite side of the outer diameter center with respect to the inner diameter center of the Efcentric Push eccentric member. Because the purpose is to set the center of gravity.

This may be done as shown in FIGS. 8 and 9.

First, Figure 8 shows the hole 6 in the Efcent link push 600.
01 and Eccentric Push 6004%lj A member 602 having a higher specific gravity than the material is provided to obtain a predetermined center of gravity position, and a hole 601 and a heavy specific gravity member 602 are provided.
may be provided individually or both may be provided together.

Next, FIG. 9 shows an E-centric push 700 configured with both a small specific gravity member 701 and a large specific gravity member 702,
This shows an arrangement in which a predetermined center of gravity position is obtained.

In the above embodiment, the E-centric push 500 is connected to the scroll member 24 (
Although the case is shown in which the radial needle bearing 26 is inserted into the boss 243 (see FIG. 2, FIG. 3, and FIG. 4) of the
Although the F-centric push 500 was directly inserted into the crank bin 23 so that it could rotate freely, it is necessary to insert a needle between the crank bin 23 and the F-centric push 1500.
A bearing member such as a main bearing may also be inserted.

In addition, in order to smoothly slide between the Efcentric Link Push and a mating member to which it is combined, such as a crank bin, grooves for so-called oil pools are provided on the outer and/or inner diameter surfaces of the Efcentric Link Push. FIG. 10 shows an example in which an oil groove 801 is provided on the outer diameter side.

Note that the inner diameter side and the outer diameter side may be communicated through one or more holes, and the oil may be evenly sent to the inner and outer diameters through the holes.

Furthermore, instead of installing the oil groove on the inner or outer diameter side of the Efcentric Push, it may be provided on the outer diameter of the crank bin or on the boss 243 of the scroll member 24, and it also lubricates the Efcentric Push. For this reason, an oil hole may be provided in the main shaft 17 and the crank bottle 23, and lubricating oil may be supplied to the e-centric push through this hole.

FIG. 11 shows a second embodiment of the present invention, in which the main shaft 17
is provided with a boss 902 having a concave portion 901 in which the Efcentric link pusher 900 is inserted, and the scroll member 24 is provided with a boss 902 on the disc 241, and the Efcentric link pusher 900 is inserted into the boss 902.
00 has a shaft 903 protrudingly inserted into its outer diameter, and an efficient link push 900 is rotatably inserted between the boss 902 and the shaft 903 in both members. The thrust needle bearing has been omitted here, but as mentioned above,
It may or may not be attached, and the same applies to oil grooves and oil holes.

In short, according to the present invention, when the center of the inner diameter and the center of the outer diameter are eccentric, the eccentric bush having a center of gravity on the opposite side of the center of the outer diameter with respect to the center of the inner diameter is connected to the crank pin of the main shaft via the spring. It is rotatably inserted between the side of the revolving scroll member and the eccentric rotation of the crank bin, and the orbital radius of the revolving scroll member with respect to the stationary scroll member is determined by the rotation of the IJ rack shaft. The present invention is industrially extremely useful because a high-performance scroll compressor can be obtained by making it variable.

[Brief explanation of the drawings] Figure 1 is a diagram of the operating principle of a known scroll compressor, and Figure 2 is a diagram of the operating principle of a known scroll compressor.
The figure is a longitudinal cross-sectional view of a known scroll type compressor, FIG. 3 is a cross-sectional view taken along the line ■-■ in FIG. 2, and FIG.
A partial cross-sectional view showing the revolution mechanism of the embodiment, FIG. 5 is a vertical cross-sectional view of FIG. 4, and FIGS.
7 (1) to (4) are respectively explanatory diagrams of the action of FIG. 4, and FIGS. 8 and 9 are front views showing modifications of FIG. FIG. 10 is a perspective view showing an oil groove of an e-centric push, and FIG. 11 is a partial vertical sectional view showing a second embodiment of the present invention. ,,゛・□ 3...Small chamber, lO...Housing, 11...Front end brake), 12...Rear end plate, 13...
Cylinder plate, 14... Suction port, 15... Discharge port,
17... Main shaft, 23... Crank pin, 24... Revolutionary scroll member, 241... Disc, 242... Spiral body, 243... Boss, 25... Stationary scroll member, 25
1... Disk, 252... Spiral body, 26... Radial needle bearing, 53... Small chamber, 271... Square tube member, 2
91...Sliding body, 292...Ring member, 293...Stop rotation, 500...Efcentric push, 501
...i8 part, 502... Anno (Lansmas, 503
... Spring material, 51.51', 52.52'... Contact point, 600... Efcentric push, 601... Hole, 602... Gravity member, 700... Efcentric push, 70
1. Small specific gravity member, 702... Large specific gravity member, 800...
F-centric push, 801... Oil groove, 900... F-centric push, 901... Recess, 902... Boss, 903... Shaft, 904
...Spring material sub-agent Patent attorney Tadashi Tsukamoto Fumihan) ■ Flood 3 Kasumi, ¥ll) '7 Figure (2) (3) (4) Milk 6 figure 9 figure Kon 10 figure

Claims (1)

[Claims] When the center of the inner diameter Q, the center of the outer diameter, and the center of gravity are connected, an efficient link push whose center of gravity is approximately opposite to the center of the outer diameter with respect to the center of the inner diameter is connected to the crankbin side of the main shaft and the revolving scroll member side via a spring. The invention is characterized in that the revolution radius of the revolving scroll member with respect to the stationary scroll member is made variable by the rotation of the efcentric push caused by the eccentric rotation of the crank pin. Scroll compressor.