JPS58170883A - Scroll compressor - Google Patents

Abstract

PURPOSE:To reduce the mechanical loss of an Oldham's mechanism used in a scroll compressor, by employing such an arrangement that an annular Oldham's ring having a particular circumferential cross section has a radial width at the contact surfaces where the ring is held in contact with a frame and a turning vane smaller than the maximum radial width of the ring. CONSTITUTION:An Oldham's ring 16 is shaped in an annular form and has a particular circumferential cross section in the form of a barrel. That is, opposite portions 16a, 16b of the cross section where the ring 16 is held in contact with a frame 2 and a vane carrying disk 14 are made straight while two side portions 16c, 16d connecting the opposite ends of the contact portions 16a, 16b are shaped in an outwardly curved form. With such an arrangement, the Oldham's ring 16 is made to have a relatively small contact area where it is held in contact with the frame 2 and a turning vane 12 in comparison with a relatively large area of the section perpendicular to the circumference of the ring 16, so that it is enabled to reduce the mechanical loss of an Oldham's mechanism used in a scroll compressor.

Description

Detailed Description of the Invention [Technical Field of the Invention] The present invention relates to a scroll compressor, and in particular, to reduce the contact area between the frame and the orbiting scroll while maintaining sufficient strength of the Oldham ring that contacts the frame and the orbiting scroll. The present invention relates to a scroll compressor that can improve the mechanical efficiency of the compressor.

[Technical background and problems of the invention]

In general, a scroll complexor has spiral-shaped fixed scroll blades that are engaged with each other, and the gas sucked in from the suction port is confined in a compression chamber formed between the fixed scroll blade and the orbiting scroll blade, and the gas is trapped in the compression chamber formed between the fixed scroll blade and the orbiting scroll blade. Accordingly, the volume of the compression chamber is gradually reduced, and during this period, the gas is compressed into high-pressure gas, which is then discharged into the discharge chamber from a discharge port provided near the center of the spiral of the fixed scroll blade. The principle itself is well known.

In this type of compressor, F! The J-arranged scroll blade is rotated via an Oldham mechanism disposed in contact with the orbiting scroll and the frame. This Oldham mechanism is often composed of a ring-shaped Oldham ring, and the upper and lower surfaces of this Oldham ring are moved in contact with a claim and an orbiting scroll. The cross section perpendicular to the circumferential direction has a rectangular shape, and in order to maintain a predetermined strength against stress in the circumferential direction, the area of the cross section! −
If the size was increased to a certain extent, the contact area with the frame and the orbiting scroll would be large, resulting in considerable mechanical loss due to the sliding resistance.

[Purpose of the invention]

Therefore, the purpose of the present invention is to reduce the contact resistance between the Oldham ring and the orbiting scroll without reducing the strength of the Oldham ring, thereby reducing the mechanical loss caused by the contact resistance, thereby achieving an efficient scroll/hump presser. Our goal is to provide the following.

[Summary of the invention]

To achieve the above object, the present invention provides a radial width 'k of the frame and orbiting scroll contact surface of the Oldham ring.
By forming the ring to be thicker than the maximum radial width of the ring, when the cross-sectional area of the ring is the same as when the cross-sectional shape is rectangular, when the contact area with the frame and the orbiting scroll is rectangular. It is characterized by being made smaller.

[Embodiments of the invention]

Embodiments of the scroll co/breather according to the present invention will be described below with reference to the drawings.

In FIG. 1, the symbol / indicates a closed casing;
A mounting frame λ is press-fitted and fixed inside the casing. Inside this mounting frame λ, there is a storage chamber 3,
Head receiving hole≠Fuyohi bearing hole j is formed in stages. A drive shaft 6 is rotatably inserted into the bearing hole j,
The rod 7 of the upper end of the drive shaft is loosely fitted into the head receiving hole, and the lower end surface 7a of the shaft head 7 is attached to the mounting frame λ.
It is supported by a bearing type. Further, the drive shaft 6 extends downward from the cage, and its lower end is immersed in a lubricating oil reservoir stored at the bottom of the casing.

Furthermore, a rotator constituting the drive motor is fixed on the axis of the drive shaft load, while a stator io is concentrically arranged outside the rotator, and the stator 10 is connected to the casing/C)@ is maintained.

10,000, an eccentric hole is formed in the shaft head 7, which is eccentric from the axis of the drive shaft load.

This eccentric hole l/ has the entire symbol /:! If the driven shaft 13 of the orbiting scroll shown by , is loosely fitted, the driven shaft /
JK is integrally connected to the outside of the wing support disk, and an expanding scroll $13 is integrally formed on the upper surface of JK.The above-mentioned orbiting scroll wing 15 has a rectangular cross-section, /3& and the wing ventral surface 1s13. which is in a parallel relationship.
It has TSA. The above Yu support Enwa/44 is soo
It is supported by the Oldham ring/4 that touches the lower WJKi, and the lower surface IUIU of this Oldham ring/4 is in contact with the frame.

This Oldham ring 16 is shown in Figure λ at 1%, the surface shape in Figure 3 is barrel-shaped, there is no barrel shape, frame λ and wing support disk /4'
Both contact edges /4a, /6b are formed in a straight line, and λ connects both ends of these contact edges /AIL, #, t).
The two 9allk/40 and /4a are formed in a curved shape that spreads outward in the cross section. That is, both contact edges/41. The length of /At) is smaller than the maximum width of the cross section of /At). Furthermore, as is clear from FIG. 2, the contact surfaces /AN and /4bK of this Oldham ring /4 to the frameco and the orbiting scroll 12 are as follows:
Key grooves 17 and /I are formed that are orthogonal to each other. Among these, key groove /I fits with the linear key iq provided on the bottom of the storage chamber J, while the other key groove Reference numeral 17 is attached to the lower surface of the wing support disk/4C and is fitted with a key (not shown) that is orthogonal to the key/9. Therefore, due to the rotation of the driving shaft load, the driven shaft /3.

It makes a circular motion around the axis of the drive shaft load, but it makes an orbiting motion due to the action of the orbiting scroll/Ji Oldham ring/6.

Thus, above the mounting frame 2, a Sea Loud Co. is fixed so as to sandwich the orbiting scroll blade.
This sea loud U has an annular suction chamber n on the inside and outside, and further has a fixed scroll blade inside thereof, and a discharge port is opened at the center of the spiral of the fixed scroll blade. It is preferable that the fixed scroll blade is manufactured to have the same shape and size as the orbiting scroll blade 15, and to be processed so that the height of the blade is exactly the same.

Incidentally, a suction pipe penetrating the casing/and the cylinder loud V is connected to the suction chamber U. A discharge chamber is formed between the simroud 2 and the top plate of the casing, and a discharge pipe 17 is connected to the discharge room temperature.

Before this, an oil passage U is formed in the drive shaft 4, and this oil passage is connected to the inlet oil passage 9, the connecting oil passage 30, and the outlet oil passage J/. Oil road Kota entrance boat Kota V
A opens at approximately the axial center position of the drive shaft load, and the exit robot J de b opens at the above bearing hole! It opens at the lower position. In addition, the outlet oil passage 3/ is formed in a hook shape, and the inlet bow) J/IL
is the bearing hole! 3/t
is opened at a position eccentric to the axial center of the drive shaft load, and three oil sump chambers formed by a hole wall are formed below the shaft end of the driven shaft/3. Then, when the drive shaft 6 rotates, the outlet port (J/1) is in an eccentric position, so the lubricating oil passes through the entire oil supply path and enters the oil reservoir chamber 3 under the action of centrifugal force. is being supplied to.

Note that the driven shaft txt- is an oil supply passage 3 penetrating in the direction of the vertical axis.
3 is formed, and supplies a part of the lubricating oil in the oil mυ chamber 32 to an outlet that is between the sliding surfaces of the fixed scroll blade and the orbiting scroll His and that is open at the root of the orbiting scroll blade 15. The oil supply passage 33 is provided so as to communicate between the oil reservoir chamber n and the compression chamber 31A formed between the fixed scroll blade and the orbiting scroll blade lj.

Since the present invention is configured as described above, the Oldham ring 16 has a small contact area with the frame coil and the orbiting scroll blade in comparison with its strength, that is, the size of the cross-sectional area perpendicular to the same station direction. The cross-sectional height of the Oldham ring with a rectangular cross-section is kb, and the cross-sectional width is kb, which is the radial width of the contact surface between the frame and the orbiting scroll.
1, the strength against circumferential stress of this Oldham ring is determined by the cross section m area m l = b, h〇 On the other hand, in the Oldham ring 14 according to the above-mentioned embodiment of the present invention,
The width of the upper and lower edges of the cross section, that is, the radial width of the contact surface with the frame co and the orbiting scroll 12 is bl, the maximum width of the cross section, that is, the maximum radial width of the ring 16 is S1, and the ring height is h, which is the same as the conventional one. Then, the cross-sectional area of this Oldham ring/A is .

Approximate the upper and lower sides to isosceles trapezoids, respectively, and obtain the following formula: m, 2・(”t + bs )h/λ・/2= (1)
, +b, ) h/2 Here, >b, = xbt (x>
/ ) (!: I can put it down. I miss it, I miss it, I get it, (/+K) h/2 When the strength of the conventional Oldham ring and the Oldham ring according to the present invention is strong, that is, Mu1=Mu! In the case, =l)lh=Mu* = bt (/+K)h/ Therefore -ts -'bv (/+K)/K As mentioned in 5 above, while K>/, /+K> 2, i.e. (10 wards)
/ 2) Since t, from the above formula, bt>- and 11
Y, the contact width b1 of the Oldham ring according to the present invention is smaller than the contact width b1 of the conventional Oldham ring with a rectangular cross section with the 7 frames and the orbiting scroll, assuming the ring strength is the same. Possible〇Also, the above-mentioned points hold true even when the cross-sectional shape of the Oldham ring is circular. [Effects of the invention] As described above, the scroll compressor using the unexploded aAK has an Oldham mechanism that is It is formed from an annular Oldham ring with a constant cross section in the direction.

The radial width of the seven frames and the orbiting scroll contact surface of this Oldham ring is formed to be smaller than the maximum radial width of the ring, thereby reducing the contact area with the frame and the orbiting scroll while maintaining sufficient ring strength. This makes it possible to fully ensure the durability and reliability of the compressor, while completely reducing mechanical loss due to slip resistance of the Oldham ring and improving the operating efficiency of the scroll compressor.

[Brief explanation of drawings]

Fig. 1 is a vertical sectional view showing an embodiment of the scroll compressor according to the present invention, Fig. 2 is a perspective view of the Oldham ring in Fig. 1, and Fig. 3 is an enlarged view of the radial cross section of the Oldham ring. be. 12... Orbiting scroll, l Hiro... Wing support disk,
/S... Orbiting scroll blade, l... Oldham ring, /6a... Orbiting scroll contact surface, /41)...
Frame contact surface, 2/...Shijima Fukudo, Ko...Fixed scroll wing. Applicant's representative Kiyoshi Inomata 11 Tame 2 Bacteria 3rd Order 6

Claims (1)

[Scope of Claims] l) A spiral fixed scroll blade and an orbiting scroll blade are engaged with a tube, and a driven shaft of the orbiting scroll blade is loosely fitted into an eccentric hole formed at the shaft end of the drive shaft. The orbiting scroll blade is rotated relative to the fixed scroll blade through an Oldham mechanism in contact with the frame and the orbiting scroll, and gas is compressed in a compression chamber formed between both scroll blades. In a compressor; the Oldham mechanism is formed from an unusual Oldham ring having a constant cross section in the circumferential direction, and the radial width of the frame and orbiting scroll contact surface of the Oldham ring is formed to be smaller than the maximum radial width of the ring. A scroll that is characterized by the fact that: A scroll compressor according to claim 1, wherein the Oldham ring has a circular cross section perpendicular to the circumferential direction. Both the contact edges to the frame and the orbiting scroll are formed in a straight line, and the two 1I111# connecting the two contact edges are shaped into a barrel shape with a curved cross section that spreads outward. The scroll compressor according to item 1 of the scope of the present invention.