JPS59141783A - Scroll fluid machine - Google Patents

Abstract

PURPOSE:To prevent the abrasion and breakage of an Oldham ring member by a method wherein the axial clearance of the Oldham ring part is made larger in order to make the Oldham ring free into axial direction so as not to receive the axial load. CONSTITUTION:The outer peripheral part 2f of the mirror plate of a rotary scroll 2 is pinched between a frame 4, fixing a fixed scroll 1, and the mirror plate 1c of the fixed scroll 1 keeping a minute gap delta05 and the upper end face 30b of main body 30a of the Oldham ring 30 is located below the table surface 4b1 of the frame 4. The rotary scroll 2 is supported by the table 4b of the frame 4 even if the same is dropped by the gravity thereof, therefore, the gravity force of the rotary scroll 2 will never effect on the Oldham ring 30 due to the existence of the clearance delta02 in the axial direction.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to an oil-fed scroll fluid machine used as a refrigerant compressor or an air compressor for refrigeration and air conditioning, refrigerators, etc.

[Prior art]

Taking a refrigerating and air conditioning compressor as an example of an oil-supplied scroll fluid machine, its basic configuration, lubrication method, etc. will be explained with reference to FIGS. 1 to 9. For ease of explanation, solid arrows indicating the flow direction of working gas and doom arrows indicating the flow direction of lubricating oil are shown in each figure. FIG. 1 shows an example of a vertical compressor QWt, which is a closed type and has a scroll compression element section at the upper part of the main body and an electric motor section at the lower part of the main body.

FIG. 1 shows the overall structure of a conventional hermetic scroll compressor for air conditioners. The pressure #i machine has both fixed scroll member 1 and orbiting scroll member 2, which are compression element parts.
The rotation prevention member 3 that prevents rotation of the orbiting scroll 2, the ball shaft 6, and the three bearings that support this, namely,
The slewing bearing 12, the main bearing 11', the auxiliary bearing 10, the electric motor 9, the fixed scroll 1t, and the fixed stationary member 4 (hereinafter referred to as "
It is made up of parts called "frames". These components are housed inside the closed container 23. Note that FIG. 1 shows an example of a structure of a high-pressure chamber type in which the inside of the closed container 23 is placed in an atmosphere of discharge pressure (high-pressure side pressure).

The operation of the compressor will be explained according to the flow of refrigerant gas and the flow of lubricating oil.

The low-temperature, low-pressure refrigerant gas is guided from the suction pipe 19 and reaches the suction chamber 1f in the fixed scroll 1. As shown in FIG. 2, the refrigerant gas that has reached the compression element portion gradually shrinks the closed spaces 5a and 5b formed by both scrolls due to the revolving movement of the orbiting scroll, which is prevented from rotating, and moves to the center of the scroll. At the same time, the pressure of the refrigerant gas is increased and it is discharged from the central discharge hole 1d. The discharged high-temperature, high-pressure refrigerant gas flows through the upper space 16 in the closed container 1 and the passage 1.
3.14, it fills the space 17 of the electric motor 19, and is led to the outside via the discharge pipe 20. (This high discharge pressure is indicated by the symbol Pd.) On the other hand, the single-turn scroll member 2
In the space 18 (this is called the "back pressure chamber") surrounded by the back surface of the frame 4 and the seven frames 4, there is a gas force in the thrust direction due to the gas pressure in a plurality of sealed spaces formed by both rotating and fixed scrolls. (This force becomes a repulsion force that tries to push down the orbiting scroll member 2.) In order to counteract this force, a pressure (indicated by the symbol pm) between the suction pressure (low pressure side pressure) and the discharge pressure acts. To set this intermediate pressure, a 2 cm 2 d hole is provided in the end plate 2a of the orbiting scroll 2, and the gas inside the scroll, which is in the middle of compression, is guided to the back pressure chamber through the pore, and gas force is applied to the back surface of the orbit scroll. This method of applying intermediate pressure is disclosed in JP-A-53-119412 and JP-A-55-37520, so a detailed explanation will be omitted.

Next, the detailed structure of the anti-rotation member 3 is shown in FIGS. 3 and 4. An example in which the anti-rotation member 3 is composed of an eoldham ring 30 and an oldham ring 31, 32 is illustrated. This Oldham key groove part 30 is sandwiched between the orbiting scroll 2 and the frame 4 (strictly speaking, the key pedestal 4a of the half frame part), and the Oldham key 31a*3 provided in each
1b, 32a, and 32b to prevent the orbiting scroll 2 from rotating. 37 (37a, 37b) are Oldham keyways provided on the back of the orbiting scroll 2. Therefore, there are four Oldham rings (33, 34, 35,
36) is sliding.

Figures 5 and 6 are polar views of the Oldham ring, which is an anti-rotation member. FIG. 5 shows the upper end surface 30 of the main part 30a of the Oldham ring 30, as shown in FIGS. 3 and 4.
This is an embodiment in which Oldham key groove portions 30d that engage with the Oldham key are provided at two locations on each surface of the lower end surface 30G.

FIG. 6 shows an embodiment of an integrated organ ring in which the Oldham ring part 38b and the main body part 38-a are integrated.

In addition, the outer diameter of Oldham ring 30. r1 width 'or
'Thickness. Display as r.

The structure of the periphery 9 of the end plate outer periphery 2f of the orbiting scroll 2 will be explained with reference to FIGS. 7 to 9. The end plate part of the end plate part 2a of the orbiting scroll 2 has a spring board outer circumference s2LPm plate center part 2
In Figure 8, the thickness of this continuous plate is H5, which is uniform regardless of g.
Displayed in dimensions.

). In addition, the outer peripheral portion 2f of the end plate of the orbiting scroll 2 is
The frame 40 is sandwiched between the end plate outer peripheral portion 1c of the fixed scroll 1 and the frame 40 pedestal 4b with a small gap maintained therebetween. In the case of FIG. 8, the minute gap is expressed as (■(f-Hs). (Here, Hf: the dimension between the frame top surface 4C and the pedestal 4bo surface) The springboard portion 2a of the orbiting scroll 2 has a radial Oil supply passages 40 (for example, 418, 41b, etc.) are provided.These oil supply holes 41 are located in the end plate portion 1a of the fixed scroll 1.
It engages with an oil groove 42 provided in the. The orbiting scroll 2 has the end plate outer periphery 2f connected to the jump plate outer periphery I of the fixed scroll 1.
C and the frame 40 pedestal 4b,
Frame center point (or fixed scroll center point) Of
The positional relationship between the frame 4 and the orbiting scroll 2 is as shown in FIG. 7th
The figure shows a cross-sectional view of the frame 4. The frame 4 is provided with two key pedestals 4a each having a key groove 4f for attaching an Oldham key. 4e is a bolt hole for attaching the fixed suf roll 1. In this way, a space 43 is formed around the outer circumferential portion 2f of the end plate of the orbiting scroll 2 by the outer circumferential portion 1C of the end plate and the frame 4, in addition to the back pressure chamber 18 at the back of the orbiting scroll. From now on, the space 43 will be referred to as "
It is called the frame room.

Note that the structure in which the outer circumferential portion 2f of the end plate of the orbiting scroll 2 is sandwiched between the stationary members IC and 4 while maintaining a small gap is disclosed in Japanese Patent Application Laid-Open No. 142902/1983, so the structure Explanation of the purpose, effect, etc. will be omitted. Reference numerals 8 and 24 indicate balance weights, which are balancing components for canceling out the centrifugal force acting on the orbiting scroll 2, and swing around the main shaft 60.

Next, the flow of lubricating oil will be explained using FIG. 1, FIG. 7, and FIG. 8.

The lubricating oil 7 is stored in the lower part of the closed container 23.

The lower end of the main shaft 6 is immersed in the oil at the bottom of the container, and the upper part of the main shaft is provided with an eccentric shaft portion 6a. engaged. The main shaft 6 has an eccentric vertical hole 6b formed from the lower end of the main shaft to the upper end surface of the main shaft for supplying oil to each bearing section.

At the lower part of the eccentric shaft part 6a, a balance weight 8 is provided at the upper part of the main bearing facing the tip surface of the orbiting scroll boss part 2e.
It is formed to be engaged with and integrated with the main shaft 6. The lower end of the main shaft 6 immersed in the lubricating oil 7 is in an atmosphere of high discharge pressure Pd, while the rotation of the downstream swing bearing 12 is in an atmosphere of intermediate pressure Pm, so the pressure is (Pd-Pm). Due to the difference, the lubricating oil 7 at the bottom of the container rises inside the eccentric vertical hole 6b. Furthermore, due to the rotation of the main shaft 6, centrifugal force acts on the oil in the eccentric vertical hole 6b, further increasing the amount of oil supplied to each bearing. In this way, each bearing is supplied with oil by the eccentric hole oiling method and the differential pressure oiling method. Eccentric vertical hole 6
The lubricating oil 7 that has risen inside b is transferred to the auxiliary bearing 10 and the main bearing 11.
At the same time, the upper space 25 of the eccentric shaft portion 6a (the gap between the bottom surface of the boss portion of the orbiting scroll boss s2e and the upper end surface of the eccentric shaft m6a, this space becomes a hydraulic chamber.Hereinafter referred to as "Yada Royal House") 25). The lubricant in the hydraulic chamber 25 is pumped at a pressure equal to the discharge pressure Pd.
As shown in FIG. 8 and FIG.
It reaches the oil groove 42 provided in the outer peripheral part IC of the end plate of the fixed scroll. The lubricating oil that has reached the oil groove 42 reaches the frame chamber 43 or the suction chamber 1f inside the scroll. Furthermore, the lubricating oil that has reached the swing bearing 12 and the main bearing 11 is drained into the back pressure chamber 18 through the bearing gap. The lubricating oil that has reached the back pressure chamber 18 is injected into the working surface formed by both scrolls 1.2 through the pores 2C and 2d after slipping on the organ ring portion 3° and the like. Inside the wrap, it mixes with the refrigerant gas. Next, the lubricating oil is pressurized together with the refrigerant gas, and moves to the motor room 17 through the discharge hole 1d1, the discharge outlet 16, and the communication channels 13 and 14. #jh to 1! ! The lubricating oil that has reached chamber A 17 is
Due to the large space, the flow rate is greatly reduced, and due to its own weight, it falls into the paper part of the container. That is, the refrigerant gas and lubricating oil are separated in the motor room 17. The fallen lubricating oil is collected again at the bottom of the container and used to lubricate each part.

Next, the problems of the prior art will be explained using the above-mentioned FIGS. 3 and 4 and FIGS. 10 to 12.

FIG. 10 shows a frame 4, an Oldham key 31a, an Oldham ring 30, an orbiting scroll 2, and a fixed scroll 1.
A vertical cross-sectional view of the area around the Oldham ring of the scroll pressing pongee shown in an assembled state. The Oldham ring 30 rests on the Oldham key 31aQ, and the orbiting scroll 2 rests on the upper end surface 30b of the Oldham ring 30. The orbiting scroll 2 is sandwiched between the outer peripheral part 2f of the fixed scroll 1 and the end plate outer peripheral surface of the fixed scroll 1 with a gap between the frame 40 and the pedestal 4b. There is also a small space δ between the upper end surface 30b). 1
It is sandwiched in with. FIG. 10 shows an embodiment in which the upper end surface 30b of the main body portion 30a of the Oldham ring 30 is located above the pedestal surface 4b1 of the pedestal 4b of the 7-frame 4. These positional relationships are as follows:
.

, the thickness H8 of the mirror plate of the orbiting scroll 2, the depth H of the Oldham ring pedestal on the frame 4 side, the thickness h of the Oldham ring, etc.

r FIG. 10 shows a state in which the Oldham ring 30 is subjected to the gravity of the orbiting scroll 2 when the compressor is not operating.

When the compressor is driven from the state shown in FIG. 10, the following problems occur.

FIG. 11 shows the positional relationship of the Oldham ring rotary shaft immediately after the compressor is started. (The illustration of the scroll wrap part is omitted.) At the moment of starting WIh, the fixed scroll 1 and the orbiting scroll 2
Since the axial force force Fa caused by the gas pressure generated in the sealed space formed by the It is pressed downward as shown in the figure. In such a state, the force (Fa-F,) acts on the upper end surface 30b of the Oldham ring 30 and further on the lower end surface 30C, and the force is strong on the end surface 2 of the orbiting scroll 2 and the upper end surface 30b of the Oldham ring 30. Causes sliding movement with contact. For this reason, mechanical friction loss increases in the Oldham link portion, and as a result, starting torque increases. In the worst case, an abnormal axial gas force acts on the upper end surface of the Oldham ring 30, and there is a fear that the resulting excessive surface pressure will cause wear and even breakage of the Oldham ring (fatigue failure). Naturally, along with the strong contact 9 between the two members 2 and 30 at the initial stage of startup, a sound (strong impact sound) is also generated.

FIG. 12 is a longitudinal cross-sectional view showing the behavior of the orbiting scroll and the positional relationship of the Oldham ring oscillator when the compressor enters a steady state.

In a steady state, the relationship between the gas forces Fa and F is F
b) Fa, so the orbiting scroll 2 floats toward the fixed scroll 1 and is pressed against it.

Further, in a steady state, as the gas torque changes due to the gas pressure in the closed space formed by both scroll wraps, the orbiting scroll 2 closes the minute gap δ as shown in FIG. 12. Perform a turning motion while tilting within the range of 1. Therefore, the end tf130e of the upper end surface 30b of the Oldham link 30 contacts the end plate rear surface -2 of the orbiting scroll 2 with one-sided contact. In such a state, the edge load acts on the Oldham ring 30, so
This raises the problem of increased mechanical friction loss and noise generation due to uneven contact.

[Purpose of the invention]

The present invention was invented in view of the above problems, and aims to provide a scroll fluid machine that ensures reliability against wear and breakage of the Oldham ring member, improves the performance of the scroll fluid machine, and reduces noise. .

[Summary of the invention]

In order to achieve the above object, the present invention prevents the axial gas force formed by both scrolls or the gravity of the orbiting scroll from acting on the Oldham ring, which is an anti-rotation member. For this reason, the outer periphery of the springboard of the orbiting scroll is sandwiched between the frame that fixes the fixed scroll and one plate of the fixed scroll while maintaining a small gap, and the Oldham ring is The structure is such that the upper end surface of the main body is located downward. Further, in a preferred embodiment, there is always a gap between the upper end surface of the main body part of the Oldham ring and the back surface of the springboard of the orbiting scroll that opposes this, and on the other hand, the lower end surface of the main body part of the Oldham ring and the frame side that opposes this. There must always be a gap between the Oldhamuki and the seat of the base.

That is, the present invention is characterized in that the axial clearance of the Oldham ring portion is increased by 9, so that the Oldham ring receives an axial load and maintains a 7-lead state in the axial direction.

[Embodiments of the invention]

An embodiment of the present invention is shown in FIGS. 13 to 19.

FIG. 13 shows the positional relationship of the Oldham ring 30 and the rotation 9 when the compressor is stopped or when the scroll pressing machine is assembled. The Oldham ring 30 rests on the upper end surface 31a1 of the Oldham key 318 on the frame side. In order to maintain the Oldham ring 30 in a straight state in the axial direction, a gap is created so that there is always a gap between the upper end surface 30b of the main body 30H of the Oldham ring 30 and the back surface 2 of the springboard of the orbiting scroll 2 that faces this. δ. 2 will be provided. On the other hand, the gap δ is provided so that there is always a gap between the lower end surface 30C of the main body portion 30a of the Oldham ring 30 and the seating surface 4a□ of the Oldham key pedestal portion 4a on the side of the frame 4 facing thereto. The gap a. 2. Providing δo3 requires the following dimensional relationship, as shown in cross section 1-1 in FIG.

δ. 2=H2-H, -hor-δo3 ・：・・・・・・
・・・・・・・・・・・・(1) δog=hok−h. S
・・・・・・・・・・・・・・・・・・・・・・・・
...Bright... (2) Here, H2: Dimension from the upper end of the frame to the seat surface 4al of the Oldham key pedestal 4a H8: Thickness of the mirror plate of the orbiting scroll hor: Thickness of the main body 30a of the Oldham ring hok"
ff Dimension from the seat surface 4a□ of the Oldham key 31aO to the upper end surface 31a (hos) Oldham key groove depth of the Oldham ring 30 Also, in order to avoid contact between the Oldham key 32b on the orbiting scroll 2 side and the Oldham ring 30 in the axial direction, The lower end surface 32.1 of the Oldham key 32b and the upper surface 30f of the Oldham key groove portion 30d of the Oldham ring 30 facing thereto.
is a certain gap δ. 4 will be provided.

The gap 6°4 has a dimension expressed by the following equation.

δ04 = H2-Hs ”ok-hon-δoa
・−・・−・−・−(3) Here, hom: Thickness of the main body of the Oldham key groove portion 30d of the Oldham ring “hOj”01! ) Figure 14 shows the frame for fixing the fixed scroll 1.
- A minute gap δ is formed between the end plate 1c of the orbiting scroll 2 and the end plate 1c of the orbiting scroll 2. The structure is such that the rotating scroll 2 is supported by the frame 40 pedestal part 4b, and the Oldham ring 3
In this embodiment, the upper end surface 30b of the main part 30a of the frame 40 is located below the pedestal surface 4b1 of the frame 40. FIG. 14 shows the positional relationship around the Oldham ring when the scroll compressor is stopped or when assembly is completed.

Even if the orbiting scroll 2 falls downward due to its own gravity, the orbiting scroll 2 is supported by the pedestal portion 4-b of the frame 4, and there is an axial gap δ between the orbiting scroll and the Oldham ring 30. 2, the self-gravity of the orbiting scroll 2 does not act on the Oldham ring 3o. 1st
In the embodiment shown in FIG. 4, the axial clearance δ and aO203 of the Oldham ring have a 10th order relationship.

hff ”δ.2+δ.3+hor ・・・・・・・・・
・・・Rule・River・・・・・・(4) Hz = Hf +
hff ・・・・・・・・・・・・Decoy...
... Hit/Song (5) In the conventional technology 2, hff=hor
...... Hit... (6) Or H, -hor≦Hf ......
・・・・・・・・・・・・・・・・・・ Since the positional relationship in (7) is very distorted, various problems have arisen, but according to the present invention, (7 to b) The relationship between the expressions disappears. Ma/hi, 9Jc
As shown in FIG. 11 above, FIG. 14 is also a diagram showing an example of the behavior of the orbiting scroll of the present invention at the instant of startup of the scroll compressor.

The orbiting scroll 2 is pushed back downward by the axial gas force caused by the same gas pressure in the closed space (5a, 5b, etc. shown in FIG. 2) formed by both scrolls 1 and 2,
The load is not received by the Oldham ring 30, but is supported by the pedestal portion of the frame 40.

Figures 11 and 16 show an example of the behavior of an orbiting scroll when the scroll pressure machine is in steady operation, and an example of the behavior of the orbiting scroll when the scroll pressure machine is in steady operation.
This shows the positional relationship between

Even if the orbiting scroll 2 performs an orbiting motion with a certain inclination, the orbiting scroll 2 will have the above-mentioned clearance δ at the maximum in the axial direction. 5 (=Hf-H,), the orbiting scroll 2 and Oldham ring 3
0 is the gap δ. 6. They are separated via δo7 and are always in a state of no contact. According to this, the orbiting scroll 2 does not cause uneven contact with the Oldham ring 30 even during operation, so compared to the conventional technology, the performance of the pressurized rock is improved by reducing mechanical friction loss, and noise is reduced. The effects can be expected.

17 and 18 illustrate an embodiment of the invention using the integral Oldham ring 38 shown in FIG. In both figures, the position of the upper end surface 38C of the main body 538a of the integrated Oldham ring 38 is
It is located at a lower position. Also, the Oldham ring 38
There is a certain gap δ between the upper end surface 38C of the main body portion 38H and the back surface 2 of the spring plate of the orbiting scroll 2 facing thereto. 8, and p1. On the other hand, there is a gap δ between the lower end surface 38d of the main body portion 38a of the Oldham ring 38 and the pedestal surface 4a1 of the Oldham key pedestal portion 4a on the frame side opposite thereto. , so that the upper and lower end surfaces 3act38d of the Oldham ring 38 do not come into sliding contact with each other to prevent abrasion of these parts. Gap δ. 9 has a dimension shown by the following formula.

δ. e=hi -hn ・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・(8) Here,
h1 Height of the part of the Oldham key of the two-piece Oldham ring hn: Depth of the Oldham key groove on the frame side When the one-piece Oldham ring 38 is used as shown in FIG. End face 38f
There is a certain gap δ between the Oldham key groove 37M) and the groove bottom surface 37G of the orbiting scroll 2 which faces this n. Try to keep it at 1°.

The gap δ. 1o can be obtained by adjusting the dimensions of the Oldham key groove depth hI and the key height h' of the Oldham key part 38b of the integral organ ring part 38.

In this way, the axial clearance δ of the Oldham ring. 2, δo
By taking a larger value such as 3, the Oldham ring 30
, 38, even if the flatness (or waviness of the surface) of the upper end surface or lower end surface of the main body of the main body of the main body of the can. Therefore, the present invention can be expected to have the effect of partially reducing the machining accuracy of the Oldham ring itself.

The structure of the Oldham ring 3υ of the conventional machine is as shown in FIG.
G was in contact with or had a small gap between the springboard rear surface 2 of the orbiting scroll 2 and the pedestal surface 4a7 of the Oldham key pedestal 4a on the frame side. Because the orbiting scroll 2 moves (orbiting motion accompanied by displacement in the axial direction), the upper and lower end surfaces of the main body portion 30a of the Oldham ring 30 come into contact with the above-mentioned 2 and 4a1.In order to avoid this, the present invention Clearance O82 and δ with plenty of space in the axial direction. 3. It is characterized by giving δo of 7.6°8, etc. In addition, the gap δ. 2,
603 'δG? If 'δo8 is too large, there is a risk that the Oldham ring 30 will move in the axial direction, so these gaps are preferably within the range given by the following dimensions or relational expressions.

δ. 2I-1ao3#0.5ml ・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・(9) δ.

,=,U, ・・・・・・・・・・・・
・・・・・・・・・・・・・・・QQ'07 ”δ.8
==6010 ”v O,5a ・・・・・・・・・
・・・・・・・・・(B) 3 #(5~6)
(See figure) Dor: Oldham ring outer diameter FIG. 19 shows the pattern of the axial movement of the Oldham ring 30. Oldham ring 30 is Oldham ring 3
An oil film reaction force due to the oil in the back pressure chamber being caught in the sliding #30g (the relative surface between the keyway and the key part) acts on it, causing displacement in the axial direction (axial dance phenomenon). The actual dimensions listed in equations (9) to (2) are given in consideration so that the oil film reaction force does not directly act on the axial sliding surface of the Oldham ring. In other words, the axial clearance is such that an oil film reaction force due to oil contamination is not generated. The present invention is also characterized by providing the Oldham ring with an axial clearance that is sufficient to prevent extra unidirectional forces such as oil expansion reaction force (nuclear force also acts as a load on the compressor).

〔Effect of the invention〕

According to the present invention, the starting torque is reduced at θ so that the Oldham ring is not subjected to excessive axial load (especially at the initial stage of starting), which was a problem with conventional scroll fluid machines, and the Oldham ring itself is Destruction can be prevented. In addition, even in steady state, the Oldham ring is free in the axial direction with respect to the orbiting scroll, so there is no edge load effect, which reduces mechanical loss and improves the performance of the compressor as a whole. improves.

According to the present invention, the upper and lower end surfaces of the main body of the geordom ring are in a non-contact state with the orbiting scroll and the pedestal of the oldham key, which are opposed to these, so that wear on the upper and lower end surfaces of the main body can be completely prevented. It can be suppressed.

[Brief explanation of the drawing]

Figure 1 is a vertical cross-sectional view of a conventional closed scroll compressor, Figure 2 is a cross-sectional view showing the scroll in its closed state, and Figure 3 is a cross-sectional view of a conventional closed scroll compressor.
4 are a plan view and a vertical sectional view showing the positional relationship between the Oldham ring and the Oldham key, and FIGS. 5 and 6 are perspective views of the appearance of the Oldham ring. 7 and 8 are a plan view and a vertical front view showing the structure of the outer circumference of the end plate of an orbiting scroll according to the prior art, FIG. FIG. 2 is a vertical sectional view showing the positional relationship around the orbiting scroll and the Oldham ring. 13 to 18 show embodiments of the present invention. Figure 13 shows the positional relationship between the Oldham ring and the Oldham key turntable.
-1m arrow sectional view. FIGS. 14 to 19 are longitudinal sectional views showing other embodiments and showing the positional relationship between the orbiting scroll and the Oldham ring. 1...Fixed scroll 1a...Spring plate part of fixed scroll 2...Orbiting scroll 2a...Spring board part of orbiting scroll Order...Frame 6...
・Main shaft 7...Lubricating oil 9...Electric motor 10
．． 11.12...Bearing 18...Back pressure chamber 23
...Airtight container 30...Oldham ring 31
...Oldham key 38...Integrated Oldham ring 1 leap 11-t La leap 1 day-lot 0・de δLh 1 and ≠ 2
m 1 ((漉回multidirectional) 寥41ri 5th ω 3rd figure 3"rtb 7(2) 9th bacterium 10th figure i Bessho, Cb) Half 14 sides 51 wa 6q Procedural amendment (method) Display of the case 1982 Patent Application No. 14513 Name of the invention Scroll fluid machine correction person and Hagi 9J1K Patent applicant name (51Q1 Manufactured by Hitachi Co., Ltd.)
Plant agent Target of amendment Figure 13 (b) Contents of amendment As shown in the attached sheet

Claims (1)

[Claims] 1. It has a fixed scroll and an orbiting scroll, and these pair of scroll members consist of an end plate and a spiral wrap standing upright thereon, and both scroll members are engaged with each other with the wraps inside, and one The fixed scroll is fixed in a device that moves the closed space formed by both scroll members from the outside to the center, reducing the volume and compressing the fluid. The outer periphery of the end plate of the orbiting scroll is sandwiched with a small gap between the stationary member that supports the orbiting scroll and the springboard of the fixed scroll, and the upper end surface of the main body of the 1st Age Oldham ring is A scroll fluid machine 2 characterized in that the axial gas force formed by both scrolls or the self-gravity of the orbiting scroll does not act on the Oldham ring. There is always a gap between the main body of the Oldham ring and the back surface of the spring plate of the orbiting scroll that faces this, and there is always a gap between the lower end surface of the main body of the Oldham ring and the seating surface of the Oldham key pedestal on the 7th frame side that opposes this. A scroll fluid machine according to claim 1, characterized in that: 3. The Oldham ring always maintains an axial gap between the lower end surface of the Oldham key and the upper surface of the Oldham key groove portion of the Oldham ring opposing this. Scroll fluid machine. 4. The Oldham ring integrally forms a part of the Oldham key, and always maintains a gap in the Oldham key groove portion on the orbiting scroll side.
Scroll fluid machine as described in section.