JPH08219038A - Scroll type fluid machine - Google Patents

Abstract

PURPOSE: To reduce the noise and abnormal wear of the contact face to an internal element adjacent to a main shaft by disposing an annular flange, extended radially from the outer face of the main shaft, between the axial end face of an internal block and the axial end face of the internal element, and disposing a spacer removably between the annular flange and the internal element. CONSTITUTION: Axial movement regulating mechanism is constituted of an annular spacer 400, an annular flange 314C and first and second thrust plane bearings 326, 327, and these elements regulate the axial movement of a main shaft 314 in cooperation. The annular spacer 400 is selected from spacers of various thickness in order to minimize a positive allowable axial clearance G formed between the rear end face of the first thrust plane bearing 326 and the front end face of the annular flange 314c, and a positive allowable axial clearance H formed between the front end face of the second thrst plane bearing 327 and the rear end face of the annular flange 314c. Unpleasant noise and abnormal wear caused by a collision at the contact face in each clearance are thereby eliminated effectively.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine, and more particularly to a mechanism for restricting axial movement of a drive mechanism of a scroll type fluid machine.

[0002]

1 and 2 show a conventional scroll type fluid machine such as a scroll type refrigerant compressor. 1 and 2, for convenience of description, the left side of the drawings is referred to as the front end or front portion of the compressor, and the right side of the drawings is referred to as the rear end or rear portion of the compressor. As shown in FIG. 1, the compressor 300 includes a housing 310 having a front end plate 311, and a cup-shaped casing 312 fixed to the rear end of the front end plate 311 by a plurality of bolts 313. The opening 311a is the front end plate 3
11, the main shaft 314 made of steel is formed at the center of the opening 11
It penetrates through a. The open end of the cup-shaped casing 312 is covered with a front end plate 311. A contact surface between the front end plate 311 and the cup-shaped casing 312 is sealed by a first O-ring 315. The first annular sleeve 311b projects forward from the peripheral edge of the opening 311a, surrounds the front end of the main shaft 314, and forms a shaft sealing recess 311c inside. The mechanical seal member 314d replaces the shaft sealing recess 311.
It is disposed in the c and is attached around the main shaft 314. The main shaft 314 is rotatably supported by the first annular sleeve 311b via a radial needle roller bearing 316 installed in the front end of the first annular sleeve 311b. The second annular sleeve 311d projects rearward from the peripheral edge of the opening 311a and surrounds the inner end portion of the main shaft 314.

Front annular projection 321 and rear annular projection 322
An inner block 320 having a and is arranged inside the housing 310. The interior of the housing 310 is defined by the inner surface of the cup-shaped casing 312 and the back surface of the front end plate 311. The front annular convex portion 321 of the inner block 320 has a plurality of bolts 317.
Fixed to the front end plate 311 by
The second annular sleeve 31 of the front end plate 311
1d is surrounded, and the front end surface of the front annular convex portion 321 is in contact with the rear end surface of the front end plate 311. The main shaft 314 has a cylindrical rotor 314a that integrally and coaxially projects from the inner end surface of the main shaft 314. The diameter of the cylindrical rotor 314a is larger than the diameter of the main shaft 314. The cylindrical rotor 314a is rotatably supported by the inner block 320 via a radial plane bearing 325 fixed in an opening 323 formed through the center of the inner block 320. Radial plane bearing 325
Are fixed in the opening 323 by, for example, press fitting. The pin member 314b integrally projects from the rear end surface of the cylindrical rotor 314a. The axis of the pin member 314b is the axis of the cylindrical rotor 314a, that is, the main shaft 314.
A predetermined distance is offset in the radial direction from the axis line of. The electromagnetic clutch 318 arranged around the first annular sleeve 311b includes the sleeve 31 via the ball bearing 318b.
1b rotatably supported by the pulley 318a, and the electromagnetic coil 31 disposed in the annular recess of the pulley 318a.
8c and an armature plate 318d fixed to the outer end of the main shaft 314 extending from the sleeve 311b.
The main shaft 314 is connected to and driven by an external power source via an electromagnetic clutch 318.

A fixed scroll 330, a movable scroll 340, and a rotation prevention mechanism (such as Oldham coupling 350) for preventing the movable scroll from rotating while the compressor is operating are housed inside the housing 310. Has been done. The fixed scroll 330 has a circular end plate 331.
A first spiral body 332 fixed to or extending from the front surface of the circular end plate 331, and an outer peripheral wall 333 protruding forward from the outer periphery of the circular end plate 331. The outer peripheral wall 333 of the fixed scroll 330 is fixed to the rear annular protrusion 322 of the inner block 320 by a plurality of bolts 319. As a result, the rear end surface of the rear annular protrusion 322 of the inner block 320 is fixed to the outer peripheral wall 3 of the fixed scroll 330.
It is in contact with the front end face of 33. Thus, the fixed scroll 330 is fixed inside the housing 310.
The second O-ring 334 is arranged between the rear outer peripheral surface of the circular end plate 331 and the inner peripheral surface of the tubular portion 312a of the cup-shaped casing 312, and seals the contact surface between them.
Thus, by the circular end plate 331 of the fixed scroll 330 and the rear part of the cup-shaped casing 312, the first chamber 36
0 is defined. A third O-ring 324 is arranged between the rear outer peripheral surface of the rear annular convex portion 322 of the inner block 320 and the inner peripheral surface of the cup-shaped casing 312, and seals the contact surface between them. Thus, the circular end plate 331 of the fixed scroll 330 and the cup-shaped casing 31
A second chamber 370 is defined by a part of the second tubular portion 312a and the inner block 320. In addition, the inner block 320 and the tubular portion 3 of the cup-shaped casing 312.
A third chamber 380 is defined by a part of 12a and the front end plate 311.

An inflow port 310a is formed in a portion of the tubular portion 312a of the cup-shaped casing 312 that faces the second chamber 370, and communicates the second chamber 370 with the outside of the compressor 300. The outflow port 310b is formed in a portion of the tubular portion 312a of the cup-shaped casing 312 that faces the third chamber 380, and communicates the third chamber 380 with the outside of the compressor 300. A plurality of flow paths (not shown) are formed on the outer peripheral wall 333 of the fixed scroll 330 and the inner block 320.
It penetrates through the rear annular convex portion 322, is formed in the axial direction along the edges thereof, and connects the first chamber 360 and the third chamber 380. Although the flow paths are not shown, they are arranged near the hole 333a through which the shaft portion of the bolt 319 penetrates. A hole, that is, a discharge port 335 is formed in the circular end plate 331 of the fixed scroll 330 near the center of the first spiral body 332. The reed valve 336 arranged on the rear end surface of the circular end plate 331 of the fixed scroll 330 cooperates with the discharge port 335 to correspond to the pressure difference between the first chamber 360 and the central fluid pocket 390a.
The opening / closing of the discharge port 335 is controlled. A retainer 337 is provided to prevent the reed valve 336 from flexing excessively when the outlet 335 is opened. One end of the reed valve 336, together with one end of the retainer 337, is fixed to the circular end plate 331 of the fixed scroll 330 by a bolt 338.

The movable scroll 340 is disposed in the second chamber 370 and is fixed to the circular end plate 341 and the rear end surface of the circular end plate 341 or the second spiral body 3 extending from the rear end surface.
42 and 42. Second scroll 342 of movable scroll
And the first spiral body 332 of the fixed scroll 330 are offset by 180 ° in the circumferential direction and are offset by a predetermined amount in the radial direction, and are fitted while making a plurality of line contacts.
Accordingly, at least one pair of sealed fluid pockets 390 are defined between the spiral body 332 and the spiral body 342. As shown in FIG. 2, the movable scroll 3
The reference numeral 40 includes an annular boss 343 projecting forward from the center of the front end surface of the circular end plate 341. A bush 344 is rotatably disposed in the boss 343 via a radial plane bearing 345. The radial flat bearing 345 is fixed inside the boss 343 by, for example, press fitting. The bush 344 has an axial through hole 344a. The axis of the hole 344a is radially offset from the axis of the bush 344. As described above, the pin member 314b
Is integrally projected from the rear end surface of the cylindrical rotor 314a of the main shaft 314. The axis of the pin member 314b is radially offset from the axis of the cylindrical rotor 314a, that is, the axis of the main shaft 314 by a predetermined distance.

The pin member 314b is rotatably disposed in the hole 344a of the bush 344. Pin member 3
The end portion of 14b projects from the rear end surface of the bush 344,
A snap ring 346 is fixed to the end portion of the pin member 314b, and the pin member 3 in the hole 344a of the bush 344 is fixed.
The axial movement of 14b is prevented. Thus, the main shaft 314, the pin member 314b, and the bush 344 form a drive mechanism for the movable scroll. The balance weight 347 moves the movable scroll 34 in the second chamber 370.
No. 0 circular end plate 341 is provided at the front portion of the bush 3
It is connected to the front end of 44. An annular flange 314c made of, for example, steel is provided on the inner end of the main shaft 314 and the cylindrical rotor 31.
It is formed at a position that forms a boundary with 4a. The diameter of the annular flange 314c is larger than the diameter of the tubular rotor 314a.

The first thrust plane bearing 326 is fixed by a plurality of pins 326a in an annular notch 311e formed in the outer peripheral portion of the rear end surface of the second annular sleeve 311d. The rear end surface of the first thrust plane bearing 326 is
It slightly projects from the rear end surface of the annular sleeve 311d. The rear end surface of the first thrust flat bearing 326 faces the front end surface of the annular flange 314c. The rear end surface of the pin 326a is in front of the rear end surface of the first thrust plane bearing 326. The first thrust plane bearing 326 may make frictional contact with the annular flange 314c and receive a forward thrust force via the annular flange 314c. A second thrust plane bearing 32, which is substantially the same as the first thrust plane bearing 326.
7 is fixed by a plurality of pins 327a in a shallow annular recess 320a formed on the front end surface of the inner block 320 along the edge of the opening 323. The second thrust flat bearing 327 surrounds the front end of the radial flat bearing 325 and faces the rear end face of the annular flange 314c.
The front end face of the second thrust plane bearing 327 is the inner block 3
It slightly projects from the front end face of 20. The front end surface of the pin 327a is rearward of the front end surface of the second thrust flat bearing 327. The second thrust plane bearing 327 may come into frictional contact with the annular flange 314c and receive a thrust force to the rear via the annular flange 314c.

As shown in FIG. 3, the first thrust plane bearing 326 includes a first annular member 326b and a first annular member 326.
a second annular member 326c disposed on one end surface of b. The first annular member 326b is made of steel, for example,
The annular member 326c is made of phosphor bronze (softer than steel), for example. First annular member 326b and second annular member 32
6c are fixed to each other by, for example, sintering.
The first thrust plane bearing 326 further includes the second annular member 32.
A plurality of radial grooves 326 formed on the axially outer end surface of 6c.
Including d. As shown in FIGS. 2 and 3, since the second annular member 326c made of phosphor bronze faces the annular flange 314c made of steel, the first thrust flat bearing 326 has an annular shape in a soft-hard metal contact state. A frictional contact can be made with the flange 314c. As a result, the first thrust plane bearing 32
The wear resistance of the frictional contact between 6 and the annular flange 314c is increased. As shown in FIG. 3, the first annular member 326b
The thickness L ₁ of the second annular member 326c is designed to be sufficiently larger than the thickness L ₂ of the second annular member 326c. For example, the first annular member 32
The thickness L _{1 of} 6b is 1.2 mm, and the second annular member 326c is
Is designed to have a thickness L ₂ of 0.3 mm. The structure of the second thrust plane bearing 327 is similar to that of the first thrust plane bearing 32.
Since it is the same as 6, the description is omitted.

As shown in FIG. 2, the flow path 371 has a pin 3
14b and the cylindrical rotor 314a, and is formed in the axial direction. One end of the flow path 371 opens into an axial gap 372 formed between the rear end surface of the bush 344 and the front end surface of the circular end plate 341 of the movable scroll 340. The other end of the flow path 371 opens into a radial gap 381 formed between the inner peripheral surface of the second annular sleeve 311d and the outer peripheral surface of the inner end portion of the main shaft 314. Radial gap 38
1 is the annular flange 314c and the first thrust plane bearing 3
26 of the front end plate 311 through a gap 383 in the axial direction formed between the second end member 26 and the radial groove 326d formed in the axially outer end surface of the second annular member 326c of the first thrust plane bearing 326. It is connected to a space 382 defined by the annular sleeve 311d and the front annular protrusion 321 of the inner block 320. The void 382 is formed through the inner block 320 and is formed in the radial direction.
It is connected to the lower portion of the third chamber 380 via 28. A capillary member 329 is secured within conduit 328. The filter 329a is fixed to the lower end of the capillary member 329. The Oldham coupling mechanism 350, which functions as a rotation preventing device for the movable scroll 340, includes the circular end plate 341 of the movable scroll 340 and the inner block 32.
It is disposed between the rear annular convex portion 322 and the rear annular convex portion 322. By providing the Oldham coupling mechanism 350, the rotation of the main shaft 314 causes the orbiting scroll 340 to revolve without rotating.

As shown in FIG. 4, a radial plane bearing 32 is provided.
5 is a first tubular member 325a and a first tubular member 325a.
The second cylindrical member 3 which is radially surrounded by the inner peripheral surface of the
25b and. The first tubular member 325a is made of steel, for example. The second tubular member 325b is made of, for example, phosphor bronze (softer than steel). The first tubular member 325a and the second
The tubular member 325b is fixed to each other by, for example, sintering. As shown in FIG. 2, the inner peripheral surface of the second cylindrical member 325b made of phosphor bronze faces the outer peripheral surface of the cylindrical rotor 314a made of steel. Thus, the radial plane bearing 32
Reference numeral 5 denotes a cylindrical rotor 314 in a soft-hard metal contact state.
It is in frictional contact with a. As a result, the radial flat bearing 3
The wear resistance of the frictional contact between 25 and the cylindrical rotor 314a is increased. As shown in FIG. 4, the first tubular member 325a
The thickness L ₃ is designed to be sufficiently larger than the thickness L _{4 of} the second tubular member 325b. For example, the first tubular member 3
The thickness L _{3 of} 25a is designed to be 1.7 mm, and the thickness L ₄ of the second tubular member 325b is designed to be 0.3 mm. The structure of the radial plane bearing 345 is the same as that of the radial plane bearing 325.
Since it is the same as, the description will be omitted. From the viewpoints of price, weight reduction, and lubricity, the radial flat bearings 325 and 345 and the above-mentioned first and second thrust flat bearings 326 and 327 are
In general, it is superior to conventional bearings such as ball bearings.

When the movable scroll 340 revolves during operation, the line contact between the spirals 332 and 342 moves along the spiral-shaped curved surface of the spirals 332 and 342 toward the center of the spirals. As a result, the fluid pocket 390 moves to the center to reduce the volume, and the fluid (for example, refrigerant) in the fluid pocket is compressed. Refrigerant gas introduced from a component such as an evaporator (not shown) of a refrigerant circuit (not shown) through the fluid inlet 310a is transferred from the outer ends of the spiral bodies 332, 342 to the spiral body 332. Three
It is entrained in a fluid pocket 390 formed between 42. The refrigerant gas entrained in the fluid pocket 390 is compressed, passes through the discharge port 335, and is wound into the spirals 332, 34.
The fluid is discharged from the second central fluid pocket 390a into the first chamber 360. After that, the refrigerant gas in the first chamber 360 is mixed with the outer peripheral wall 333 of the fixed scroll 330 and the inner block 320.
It flows into the third chamber 380 through the above-mentioned flow path (not shown) formed in the axial direction through the rear annular convex portion 322. The refrigerant gas that has flowed into the third chamber 380 further flows through the fluid outlet 310b to other components such as a condenser (not shown) of a refrigerant circuit (not shown).

Referring to FIGS. 1 and 2, the lubricating oil accumulated at the bottom inside the first chamber 360 is the outer peripheral wall 333 of the fixed scroll 330 and the rear annular protrusion 322 of the inner block 320.
Through the above-mentioned flow path (not shown) formed in the axial direction to flow into the bottom portion inside the third chamber 380.
The lubricating oil in the bottom inside the third chamber 380 is
The pressure difference between the second chamber 370 and the conduit 328,
The void 382, the axial gap 383, or the radial groove 326d (shown in FIG. 3) of the first thrust plane bearing 326, the flow path 37.
1, through the axial gap 372 and the radial gap formed between the boss 343 and the radial plane bearing 345, and between the bush 344 and the radial plane bearing 345,
It is guided to a space 373 formed between the inner block 320 and the circular end plate 341 of the movable scroll 340. The lubricating oil guided into the space 373 flows through a position of the second chamber 370 outside the spiral wound bodies 332, 342, passes through the Oldham coupling mechanism 350, and lubricates the mechanism 350. Further, part of the lubricating oil guided to the radial gap 381 flows to the shaft sealing hole 311c, and the mechanical seal element 3
14d internal friction surface and mechanical seal element 314d
And the friction surface between the main shaft 314 and the main shaft 314 is lubricated.

Further, a part of the lubricating oil introduced to the space 382 is part of the radial groove 327d of the second thrust plane bearing 327.
Flow through (shown in FIG. 3), radial plane bearing 325
And a radial clearance formed between the outer peripheral surface of the inner block 320 and the inner peripheral surface of the opening 323 of the inner block 320.
5 and the radial gap formed between the outer peripheral surface of the cylindrical rotor 314a, and the space 37 of the second chamber 370.
Inflow to 3. Part of the lubricating oil introduced to the space 373 is
A radial gap formed between the outer peripheral surface of the radial flat bearing 345 and the inner peripheral surface of the boss 343, and the radial flat bearing 3
It flows into the axial gap 372 through the radial gap formed between the inner peripheral surface of 45 and the outer peripheral surface of the bush 344. As described above, since the lubricating oil flows from the bottom inside the third chamber 380 to the second chamber 370, the friction surface of the internal member of the compressor, such as the friction surface between the bush 344 and the radial plane bearing 345, is not generated. Effectively lubricated by lubricating oil.

[0015]

In the above configuration,
When assembling the compressor, it is necessary to provide a positive axial allowance gap between the following adjacent surfaces to prevent undesired interference between the adjacent surfaces. (A) An adjacent surface of the bush 344 and the circular end plate 341 of the movable scroll 340. (B) Adjacent surface of the balance weight 347 and the boss of the movable scroll 340. (C) Balance weight 347 and Oldham coupling 35
Adjacent to 0. (D) An adjacent surface between the balance weight 347 and the internal block 320. (E) Annular flange 314c and annular sleeve 311d
The adjacent surface to. (F) An adjacent surface between the annular flange 314c and the inner block 320. Further, unlike conventional bearing devices such as radial ball bearings that include an inner race, an outer race, and a plurality of balls rotatably disposed between the races, the main shaft 314 and the radial plane bearings 325, 345 differ from each other. There is no blocking element for blocking the axial movement of the main shaft 314 between the main shaft 314 and the radial needle roller bearing 316. As a result, during operation of the compressor 300, the main shaft 314 will have radial plane bearings 325, 34 due to the positive axial tolerance clearance described above.
5 slides back and forth along the inner peripheral surface of No. 5 and the inner peripheral surface of the radial needle roller bearing 316.

As a result, during operation of the compressor 300, the main shaft 3
When 14 moves rearward, the above-mentioned adjacent surface (A),
One of (B), (C), and (F) that has the smallest positive axial tolerance clearance may collide. Spindle 3
When 14 moves forward, one of the adjacent surfaces (D) and (E), which has the smallest positive axial allowance, may collide. These collisions can cause unpleasant noise and abnormal wear of the collision surface. As shown in FIG. 2, in order to prevent the above-mentioned defects, a first thrust flat bearing 326 and a second thrust flat bearing 327 are provided on the rear end surface of the second annular sleeve 311d and the front end surface of the inner block 320, respectively. Is provided. Furthermore,
The positive allowable axial gap 383 formed between the front end surface of the annular flange 314c and the rear end surface of the first thrust plane bearing 326 is larger than the positive allowable axial gap formed between the adjacent surfaces (D). Is also designed to be small. The positive allowable axial gap formed between the rear end surface of the annular flange 314c and the front end surface of the second thrust flat bearing 327 is formed between the adjacent surfaces (A), (B) and (C). It is designed to be smaller than the positive allowable axial clearance. As a result, the forward movement and the backward movement of the main shaft 314 are restricted by the first thrust plane bearing 326 and the second thrust plane bearing 327, respectively. Since the first thrust plane bearing 326 and the second thrust plane bearing 327 are configured as shown in FIG. 3, unpleasant noise and abnormal wear are reduced.

However, the positive allowable axial gap 383 formed between the front end face of the annular flange 314c and the rear end face of the first thrust plane bearing 326 is the inner block 320 having the front annular protrusion 321 and the 2 annular sleeve 311d
Due to the limit of accuracy in machining the front end plate 311 having the above and the main shaft 314 having the annular flange 314c, for example, about 0.1 mm to 0.5 mm,
It becomes relatively large. Similarly, the positive allowable axial gap formed between the rear end surface of the annular flange 314c and the front end surface of the second thrust flat bearing 327 is, for example, 0.1 mm to 0. It is relatively large, about 5 mm. Thus, between the annular flange 314c and the first thrust plane bearing 326, and the annular flange 3
Unpleasant noise and abnormal wear at the contact surface between 14c and the second thrust bearing 327 are not sufficiently reduced. The present invention has been made in view of the above problems, and the unpleasant noise and abnormal wear caused by the collision at the contact surface between the spindle and the internal elements adjacent to the spindle in the axial direction have been sufficiently reduced. An object is to provide a scroll type fluid machine. Another object of the present invention is to reduce the manufacturing cost and weight of the compressor and to increase the durability.

[0018]

In order to solve the above problems, in the present invention, a housing, a first end plate disposed in the housing, and a first spiral member extending from the first end plate. A fixed scroll having a second end plate, and a movable scroll having a second end plate and a second spiral body extending from the second end plate.
The first spiral member and the second spiral member are fitted in a circumferentially and radially offset manner to form a plurality of line contacts defining at least a pair of sealed fluid pockets, and
A drive mechanism axially disposed in the housing and having a main shaft operatively connected to the movable scroll to revolve the movable scroll; and a drive mechanism fixed in the housing to allow a part of the main shaft to rotate. An inner block that supports the inner scroll, an inner element that is disposed in the housing at a distance from the inner block in the axial direction, and an inner element that is connected to the movable scroll, and the movable scroll rotates when the movable scroll revolves. And a rotation preventing mechanism for reducing the volume of the fluid pocket, and an axial movement restricting mechanism for restricting the axial movement of the drive mechanism. An annular flange extending radially from the outer surface of the main shaft and arranged between the axial end surface of the inner block and the axial end surface of the inner element; and the annular flange. Providing scroll fluid machine characterized in that it comprises a spacer disposed detachably between Nji and the inner element.

Further, in the present invention, a fixed scroll having a housing, a first end plate and a first spiral body extending from the first end plate, the fixed scroll being provided in the housing, and the fixed scroll provided in the housing. A movable scroll having a second end plate and a second spiral body extending from the second end plate, wherein the first spiral body and the second spiral body are fitted to each other with offset in the circumferential direction and the radial direction. Together to form a plurality of line contacts defining at least one pair of sealed fluid pockets, further disposed axially within the housing and operatively coupled to the movable scroll. A drive mechanism having a main shaft that revolves around an inner block, an inner block that is fixed in the housing and rotatably supports a part of the main shaft, and an axial direction in the housing and from the inner block. An anti-rotation mechanism, which is connected to the movable scroll and an internal element disposed at a distance to prevent the movable scroll from rotating when the movable scroll revolves to reduce the volume of the fluid pocket. And an axial movement restricting mechanism for restricting axial movement of the drive mechanism, the axial movement restricting mechanism extending in a radial direction from an outer surface of the spindle, and an axial end surface of the inner block and the A scroll-type fluid machine comprising: an annular flange disposed between the inner end portion and an axial end surface of the inner element; and a spacer detachably disposed between the annular flange and the inner block. I will provide a.

In a preferred aspect of the present invention, the axial movement restricting mechanism further includes a first thrust flat bearing disposed between the annular flange and an axial end surface of the inner block, and the annular flange. And a second thrust flat bearing disposed between the spacer and the spacer. In a preferred aspect of the present invention, the spacer is made of steel. In a preferred aspect of the present invention, the first thrust plane bearing includes a first annular element made of steel and a second annular element made of phosphor bronze.
An annular element, the second annular element is disposed on an end surface of the first annular element, and the end surface of the second annular element faces the annular flange. In a preferred aspect of the present invention, the axial movement restricting mechanism is arranged at least partially in an oil passage defined by the spindle and the internal block. In a preferred aspect of the present invention, the housing hermetically houses the drive mechanism.
In a preferred aspect of the present invention, the drive mechanism further includes a motor that is connected to the main shaft and rotates the main shaft.

[0021]

In the present invention, the axial movement restricting mechanism for restricting the axial movement of the drive mechanism is provided, and the axial movement restricting mechanism extends in the radial direction from the outer surface of the main shaft and the shaft of the inner block. Since it includes an annular flange disposed between the end face in the axial direction and the axial end face of the internal element, and a spacer detachably disposed between the annular flange and the internal element, it is possible to obtain various thicknesses in advance. Prepare a spacer, and measure the axial distance between the axial end surface of the internal block and the axial end surface of the internal element, the thickness of the annular flange, etc., prior to the assembly of the scroll fluid machine. By selecting the spacer with the optimum thickness based on the measurement results, the axial clearance between the annular flange and the axial end surface of the internal block,
Also, the axial clearance between the annular flange and the axial end surface of the internal element can be set to a minute value. This allows
The unpleasant noise and abnormal wear caused by the collision at the contact surface between the main shaft and the internal element adjacent to the main shaft in the axial direction are sufficiently reduced, and the durability of the scroll fluid machine is improved.

Further, in the present invention, an axial movement restricting mechanism for restricting the axial movement of the drive mechanism is provided,
The axial movement restriction mechanism extends in the radial direction from the outer surface of the main shaft, and is disposed between the axial end surface of the internal block and the axial end surface of the internal element, and the annular flange, the annular flange and the internal block. Since spacers that are removably disposed are included between the spacers, spacers of various thicknesses are prepared in advance, and the axial end faces of the internal blocks and the axial direction of the internal elements are arranged before the scroll fluid machine is assembled. By measuring the axial distance to the end face, the thickness of the annular flange, etc., and selecting the spacer with the optimum thickness based on these measurement results, the distance between the annular flange and the axial end face of the inner block can be The axial clearance and the axial clearance between the annular flange and the axial end surface of the internal element can be set to very small values. As a result, unpleasant noise and abnormal wear caused by the collision at the contact surface between the main shaft and the internal element adjacent to the main shaft in the axial direction are sufficiently reduced, and the durability of the scroll fluid machine is improved. .

[0023]

EXAMPLE FIG. 5 shows a scroll type fluid machine according to a first example of the present invention. In FIG. 5, elements corresponding to those shown in FIGS. 1 and 2 are designated by the same reference numerals, and detailed description thereof will be omitted. Further, in FIG. 5, for convenience of explanation, the left side of the drawing is referred to as the front end or front portion of the compressor, and the right side of the drawing is referred to as the rear end or rear portion of the compressor. As shown in FIG. 5, the axial movement restriction mechanism includes an annular spacer 400 and an annular flange 31.
4c and the first and second thrust plane bearings 326 and 327. These elements work together to make the spindle 3
The axial movement of 14 is restricted. The annular spacer 400 is
It is arranged between the front end surface of the first thrust flat bearing 326 and the rear end surface of the second annular sleeve 311d of the front end plate 311. The annular spacer 400 is formed by, for example, a plurality of countersunk screws 401, and the second annular sleeve 31.
It is detachably attached to the rear end face of 1d. The end surface of the head of the countersunk screw 401 is preferably positioned slightly forward of the rear end surface of the annular spacer 400. First
The thrust plane bearing 326 is fixed to the rear end surface of the spacer 400 by a plurality of pins 326a. Spacer 4
The outer diameter of 00 is substantially the same as the outer diameter of the first thrust flat bearing 326, and the inner diameter of the spacer 400 is preferably slightly smaller than the inner diameter of the first thrust flat bearing 326.

A positive allowable axial gap (G) formed between the rear end surface of the first thrust flat bearing 326 and the front end surface of the annular flange 314c, the front end surface of the second thrust flat bearing 327 and the annular flange 314c. In order to minimize the positive allowable axial clearance (H) formed with the rear end face, the annular spacer 400 is selected from among spacers having various thicknesses in the following procedure. First, before assembling the compressor, the following distances (Q), (R) and (S) are measured. (Q) is the front annular convex portion 3 of the inner block 320.
21 is the distance between the front end face of 21 and the bottom end face of the shallow annular recess 320a. (R) is the front end plate 31
It is the distance between the rear end face of the first annular sleeve 311d and the rear end face of the first annular sleeve 311d. (S) is the distance between the front end surface of the annular flange 314c and the rear end surface of the annular flange 314c, that is, the thickness of the annular flange 314c.

Next, an annular spacer 4 having a thickness (T)
00 is selected by calculating (T) based on the following equation. (T) = (Q)-(R)-(S) -2 (U) In the above formula, (U) represents either one of the substantially same first and second thrust plane bearings 326, 327. , Equal to the thickness including the positive tolerance. When the compressor 300 is assembled, the annular spacer 400 having a thickness (T) is detachably attached to the rear end surface of the second annular sleeve 311d of the front end plate 311 by, for example, a plurality of countersunk screws 401.

Therefore, the positive allowable axial gap (G) formed between the rear end surface of the first thrust flat bearing 326 and the front end surface of the annular flange 314c is substantially the same as that of the first and second thrust flat bearings. Equal to twice the positive tolerance of either 326 or 327. Similarly, the positive permissible axial gap (H) formed between the front end face of the second thrust flat bearing 327 and the rear end face of the annular flange 314c also has substantially the same first and second thrust flat bearings 326, Equal to twice the positive tolerance of any one of 327. Furthermore, since it is desirable that the substantially identical first and second thrust plane bearings 326 and 327 are standard products, a positive allowable axial clearance (G),
(H) is reduced to, for example, about 0.01 mm to 0.05 mm. Gap (G), (H) is about 0.01mm
It is even better if it is about 0.03 mm. Therefore, the unpleasant noise and abnormal wear caused by the collision at the contact surfaces between the annular flange 314c and the first thrust flat bearing 326 and between the annular flange 314c and the second thrust bearing 327 are effectively performed. To be removed. In this embodiment, the annular spacer 400 is replaced by the first thrust plane bearing 32.
6 is arranged between the front end surface of the second annular sleeve 311d and the rear end surface of the second annular sleeve 311d, the annular spacer 400 is arranged between the rear end surface of the second thrust plane bearing 327 and the front end surface of the inner block 320. May be.

6 and 7, according to a second embodiment of the present invention,
1 illustrates a scroll type fluid machine such as a motor driven scroll type refrigerant compressor. 6 and 7, for convenience of explanation, the left side of the drawings is referred to as the front end or front portion of the compressor, and the right side of the drawings is referred to as the rear end or rear portion of the compressor. The overall structure of the motor-driven scroll type refrigerant compressor is shown in FIG. The compressor 10 includes a housing 11 that includes a scroll type fluid compression mechanism 20 and a compression mechanism such as a drive mechanism 30.
including. The housing 11 includes a tubular portion 111, a first portion,
Second cup-shaped portions 112 and 113 are included. The open end of the first cup-shaped portion 112 is
It is detachably and airtightly connected to the front open end of the cylindrical portion 111. The open end of the second cup-shaped portion 113 is
A plurality of bolts 13 are detachably and airtightly connected to the rear opening end of the tubular portion 111. Details of connecting the first cup-shaped portion 112 to the tubular portion 111 and the second cup-shaped portion 113 to the tubular portion 111 are detailed in US Pat. No. 5,312,234. Therefore, the description is omitted.

The scroll type fluid compression mechanism 20 includes a fixed scroll 21 having a circular end plate 21a and a spiral wound body 21b extending rearward from the circular end plate 21a. The circular end plate 21 a of the fixed scroll 21 is fixed in the first cup-shaped portion 112 by a plurality of bolts 14.
The inner block 23 is press-fitted into the housing 1, for example.
It is fixed to the front open end of the tubular portion 111. The outer edge of the rear end surface of the inner block 23 is in contact with an annular projecting portion 111 a formed on the inner peripheral surface of the tubular portion 111. The scroll type fluid compression mechanism 20 further includes a circular end plate 22a and a spiral wound body 2 extending forward from the circular end plate 22a.
2b. The spiral scroll 21b of the fixed scroll 21 is offset in the circumferential direction and the radial direction, and the spiral scroll 22b of the movable scroll 22 is offset.
It is fitted with. A sealing element 211 is disposed on the end surface of the spiral scroll 21b of the fixed scroll 21, and seals the contact surface between the spiral scroll 21b of the fixed scroll 21 and the circular end plate 22a of the movable scroll 22. Similarly, the sealing element 221 is the spiral scroll 22 of the orbiting scroll 22.
It is disposed on the end surface of b and seals the contact surface between the spiral scroll 22b of the movable scroll 22 and the circular end plate 21a of the fixed scroll 21. O-ring 40 is fixed scroll 2
The outer peripheral surface of the first circular end plate 21a and the first cup-shaped portion 112
Is disposed between the circular end plate 21a of the fixed scroll 21 and the first cup-shaped portion 112 to seal the contact surface. The circular end plate 21a of the fixed scroll 21 and the first
The cup-shaped portion 112 defines the discharge chamber 50.

A discharge port 21c is formed in the circular end plate 21a of the fixed scroll 21 so as to penetrate therethrough in the axial direction.
Are connected to a central fluid pocket (not shown) defined by a fixed scroll 21 and a movable scroll 22. A reed valve (not shown) is associated with the discharge port 21c on the front end face of the circular end plate 21a of the fixed scroll 21, and the discharge port 21c corresponds to the pressure difference between the discharge chamber 50 and the central fluid pocket. Control the opening and closing of. Retainer 21
d is associated with the reed valve, and prevents excessive bending of the reed valve when the discharge port 21c is opened. The reed valve is fixed to the circular end plate 21a of the fixed scroll 21 by the screw 21e together with the retainer 21d. The first cup-shaped portion 112 includes a cylindrical convex portion 112a protruding forward from the outer surface of the front end portion. The compressed fluid flows from the central fluid pocket into the discharge chamber 50 through the valve-mounted discharge port 21c. An axial hole 112b that functions as an outlet of the compressor 10 is formed in the center through the cylindrical convex portion 112a, and through a pipe (not shown), an element such as a condenser (not shown) is formed. It is connected to the inlet. Therefore, the compressed fluid in the discharge chamber 50 is
It flows through 2b and the pipe to the inlet of the condenser of the refrigerant circuit.

The movable scroll 22 further includes a circular end plate 2
It includes an annular boss 22c protruding rearward from the central portion of 2a. The bush 60, through the radial plane bearing 70,
It is rotatably arranged in the boss 22c. The radial flat bearing 70 is fixed in the boss 22c by, for example, press fitting. The bush 60 has a through hole 60a in the axial direction. The axis of the hole 60a is radially offset from the axis of the bush 60.

The drive mechanism 30 includes a main shaft 31 and a motor 32 surrounding the main shaft 31. The main shaft 31 is a cylindrical rotor 31 a that integrally and coaxially projects from an inner end surface of the main shaft 31.
It has. The diameter of the cylindrical rotor 31 a is larger than the diameter of the main shaft 31.

The inner block 23 includes a front annular convex portion 231 protruding from the front end surface thereof. The front annular convex portion 231 surrounds the boss 22c, and the Oldham coupling mechanism 24
Form a part of. The tubular portion 11 of the housing 11
An opening 232 concentric with the longitudinal axis of No. 1 is formed through the central portion of the inner block 23. The cylindrical rotor 31 a of the main shaft 31 is rotatably supported by the inner block 23 via a radial plane bearing 80 fixed in the opening 232. The radial flat bearing 80 is fixed in the opening 232 by, for example, press fitting. The pin 31b integrally projects from the front end surface of the cylindrical rotor 31a. The axis of the pin 31 is offset in the radial direction by a predetermined distance from the axis of the cylindrical rotor 31a, that is, the axis of the main shaft 31. As shown in FIG. 7, the pin 31b is rotatably arranged in the hole 60a of the bush 60. The end of the pin 31b extends forward beyond the front end face of the bush 60, and a snap ring 601 is fixed to the end of the pin 31b to prevent axial movement of the pin 31b within the hole 60a of the bush 60. There is. The balance weight 602 is arranged in a cylindrical recess 233 formed in the center of the front end surface of the inner block 23. The balance weight 602 is connected to the rear end portion of the bush 60. The annular flange 31c is the cylindrical rotor 3
It is formed on the outer surface of the main shaft 31 at the rear of the la 1a, and is installed in a cylindrical recess 234 formed at the center of the rear end surface of the inner block 23. The diameter of the annular flange 31c is larger than the diameter of the tubular rotor 31a. The circular plate 25 is fixed to the rear end surface of the inner block 23 by a plurality of bolts 28. Thus, the tubular recess 234 is closed by the disc 25, so that a tubular chamber 235 is defined.
A hole 25a through which the main shaft 31 penetrates is formed in the disc 25. The hole 25a surrounds the main shaft 31 with a slight radial gap.

As shown in FIG. 6, the second cup-shaped portion 11
3 includes a cylindrical convex portion 113a protruding forward from the central portion of the inner surface of the bottom end portion. The cylindrical convex portion 113a is concentric with the longitudinal axis of the second cup-shaped portion 113. The radial needle roller bearing 26 is fixed in the cylindrical convex portion 113a and rotatably supports the rear end portion of the main shaft 31. Second cup-shaped portion 11
3 further includes a cylindrical convex portion 113b protruding rearward from the central portion of the outer surface of the bottom end portion. An axial hole 113c that functions as an inlet of the compressor is formed in the center through the cylindrical convex portion 113b, and an evaporator (not shown) of a refrigerant circuit (not shown) is provided through a pipe (not shown). Connected to other elements such as (not shown). The diameter of the axial hole 113c is slightly smaller than the inner diameter of the cylindrical convex portion 113a, but slightly larger than the outer diameter of the main shaft 31. The cylindrical convex portion 113d projects rearward from the peripheral edge portion of the outer surface of the bottom end portion of the second cup-shaped portion 113. A part of the cylindrical convex portion 113d is formed by the cylindrical convex portion 11
It is integral with part of 3b. The airtight seal base 27 is fixed to the rear end of the cylindrical convex portion 113d with a plurality of bolts (not shown). The O-ring 43 has the cylindrical protrusion 11
It is disposed on the rear end surface of 3d and seals the contact surface between the airtight seal base 27 and the cylindrical convex portion 113d. One end of the electric wire 27a is connected to the motor 32, and the other end penetrates the airtight seal base 27 and is connected to an external power source (not shown).

The motor 32 includes an annular rotor 32a fixed around the outer surface of the main shaft 31, and an annular stator 32b surrounding the rotor 32a with a slight gap. The stator 32b includes a second annular protrusion 111b formed on the inner peripheral surface of the tubular portion 111 and a third annular protrusion 113e formed on the inner peripheral surface of the second cup-shaped portion 113. The rear opening end portion of the tubular portion 111 and the second cup-shaped portion 113
Axially along with the open end portion of the. The second annular protrusion 111b is positioned behind the first annular protrusion 111a. The axial length of the stator 32b is slightly smaller than the axial length between the second annular protruding portion 111b and the third annular protruding portion 113e. When assembling the compressor, the stator 32b is press-fitted into the rear open end of the tubular portion 111 until the outer edge portion of the front end surface of the stator 32b comes into contact with the side wall of the second annular protrusion 111b, or The outer edge of the rear end face is pressed into the open end of the second cup-shaped portion 113 until it comes into contact with the side wall of the third annular protrusion 113e.

The main shaft 31 further includes a first axial hole 31d penetrating the main shaft 31 and extending in the axial direction. One end of the first axial hole 31d opens on the rear end surface of the main shaft 31 and is adjacent to the front open end of the axial hole 113c. First axial hole 31d
The other end of the disk ends at the rear position of the disk 25. A plurality of first radial holes 31e are formed at the front end of the first axial hole 31d, and the front end of the first axial hole 31d is connected to the internal space 111c of the tubular portion 111 of the housing 11. The second axial hole 31f extends axially from the front end of the first axial hole 31d and terminates at the center of the cylindrical rotor 31a of the main shaft 31. The diameter of the second axial hole 31f is smaller than the diameter of the first axial hole 31d, and the second axial hole 31f is concentric with the first axial hole 31d. 2nd radial hole 31g
Extends radially from the front end of the second axial hole 31f and ends at the outer peripheral surface of the cylindrical rotor 31a. The third axial hole 31h extends in the axial direction from the front end surface of the pin 31b,
It is substantially terminated at the center of the radial hole 31g. The diameter of the third axial hole 31h is substantially equal to the diameter of the second axial hole 31f, and the axis line of the third axial hole 31h is the second axial hole 31f.
It is offset in the radial direction from the axis of. Axial flow path 3
1i is formed on the peripheral portion of the cylindrical rotor 31a, and connects the radially outer end of the second radial hole 31g to the cylindrical chamber 235. A flow path 236 is formed so as to penetrate the disc 25 and the rear end portion of the inner block 23, and forms a cylindrical space 235 in the inner space 111.
It is connected to c. A plurality of conduits 237 are formed at the radial end of the inner block 23, and an inner cavity 111c is formed in the first cup-shaped portion 112 between the circular end plate 21a and the inner block 23. It is connected to 241.

The fluid is supplied from an external source, such as an evaporator,
It flows into the internal space 111c through the axial hole 113c, the first axial hole 31d of the main shaft 31, and the first radial hole 31e. The fluid in the inner space 111c is further fed to the conduit 23
7 to the internal space 241 and then entrained in the radially outer fluid pocket formed by the orbiting scroll 22 and the fixed scroll 21. The fluid in the fluid pocket moves to the center between the scrolls while reducing the volume, and is discharged into the discharge chamber 50 through the discharge port 21c to which the valve of the fixed scroll 21 is attached.

As shown in FIG. 7, the axial movement restricting mechanism includes an annular spacer 700, an annular flange 31c, and first and second thrust flat bearings 91 and 92.
These elements cooperate to regulate the axial movement of the main shaft 31. The first thrust plane bearing 91 has a plurality of pins 91.
the inner block 2 along the periphery of the opening 232.
3 is fixed in a shallow annular recess 238 formed on the rear end face of the No. 3. The first thrust plane bearing 91 surrounds the rear end portion of the radial plane bearing 80. The rear end surface of the first thrust flat bearing 91 faces the front end surface of the annular flange 31c and slightly projects from the rear end surface of the inner block 23. The rear end surface of the pin 91a is the first thrust plane bearing 9
It is desirable to be slightly forward of the rear end face of No. 1. First
The thrust flat bearing 91 may come into frictional contact with the annular flange 31c and receive a forward thrust force via the annular flange 31c. The annular spacer 700 is preferably arranged between the rear end surface of the second thrust flat bearing 92 and the front end surface of the disc 25. The annular spacer 700 is detachably attached to the front end surface of the disc 25 by a plurality of countersunk screws 701, for example. The front end surface of the head of each countersunk screw 701 is preferably rearward of the front end surface of the annular spacer 700. The second thrust plane bearing 92 is fixed to the front end surface of the spacer 700 by a plurality of pins 92a. The outer diameter of the spacer 700 is slightly larger than the outer diameter of the second thrust plane bearing 92, and the inner diameter of the spacer 700 is slightly smaller than the inner diameter of the second thrust plane bearing 92.

In this embodiment, when assembling the compressor, a positive permissible axial gap is formed between the following adjacent surfaces to prevent undesired interference between those surfaces. (A ') An adjacent surface of the pin 31b of the main shaft 31 and the circular end plate 22a of the movable scroll 22. (B ') Adjacent surface of balance weight 602 and Oldham coupling mechanism 24. (C ') An adjacent surface of the balance weight 602 and the boss 22c of the movable scroll 22. (D ') Adjacent surface between the balance weight 602 and the inner block 23. (E ') Annular flange 31c and first thrust plane bearing 9
Adjacent surface to 1. (F ') Annular flange 31c and second thrust plane bearing 9
Adjacent surface with 2. Further, unlike a conventional bearing device such as a radial ball bearing including an inner race, an outer race, and a plurality of balls rotatably arranged between the races, the main shaft 31 and the radial plane bearings 70, 80 are different from each other. There is no blocking element for blocking the axial movement of the main shaft 31 between the main shaft 31 and the radial needle roller bearing 26. As a result, the compressor 1
During operation of 0, the main shaft 31 slides back and forth along the inner peripheral surfaces of the radial plane bearings 70 and 80 and the inner peripheral surface of the radial needle roller bearing 26 due to the above-mentioned positive axial allowance clearance. To do. In this embodiment, the positive allowable axial gap formed between the adjacent surfaces (E ') is the positive axial gap formed between any of the adjacent surfaces (A'), (B ') and (C'). It is designed to be smaller than the allowable axial clearance of. Therefore, when the main shaft 31 moves forward during the operation of the compressor 10, the adjacent surface (E ′)
There may be collisions between them. The positive allowable axial gap formed between the adjacent surfaces (F ') is designed to be smaller than the positive allowable axial gap formed between the adjacent surfaces (D'). Therefore, when the main shaft 31 moves rearward during the operation of the compressor 10, a collision may occur between the adjacent faces (F ′).

In order to minimize the positive permissible axial clearance between adjacent surfaces (E ') and the positive permissible axial clearance between adjacent surfaces (F'), annular spacer 700 follows the procedure below. , Spacers having various thicknesses. First, before assembling the compressor 10, the following distances (V) and (W) (shown in FIG. 7) are measured. (V) is the distance between the bottom end surface of the annular recess 238 and the rear end surface of the inner block 23. (W) is the distance between the front end surface of the annular flange 31c and the rear end surface of the annular flange 31c, that is, the thickness of the annular flange 31c. Next, after calculating (T ') based on the following equation, the annular spacer 700 having the thickness (T') is selected. (T ′) = (V) − (W) −2 (U) In the above formula, (U) is a positive value of either one of the substantially identical first and second thrust plane bearings 91 and 92. Equal to the thickness including tolerance. The annular spacer 700 having a thickness (T ′) is detachably attached to the front end face of the disk 25 by, for example, a plurality of countersunk screws 701 when the compressor 10 is assembled. Therefore, the first thrust plane bearing 9
The positive permissible axial gap (E ') formed between the rear end face of the first annular flange 31c and the front end face of the annular flange 31c has substantially the same first,
It is about twice the positive tolerance of either one of the second thrust plane bearings 91 and 92. Similarly, the positive permissible axial gap (F ′) formed between the front end face of the second thrust flat bearing 92 and the rear end face of the annular flange 31 c has substantially the same first and second thrust flat bearings 91. , 92, which is about twice the positive tolerance. Furthermore, since it is desirable that the substantially identical first and second thrust plane bearings 91 and 92 are standard products, a positive allowable axial clearance (E ′),
(F ′) is reduced to, for example, about 0.01 mm to 0.05 mm. The gaps (E ') and (F') are about 0.0
It is even better if it is about 1 mm to 0.03 mm. Therefore,
Unpleasant noise and abnormal wear caused by collisions between the contact surfaces between the annular flange 31c and the first thrust flat bearing 91 and between the annular flange 31c and the second thrust bearing 92 are effectively removed. It In the present embodiment, the annular spacer 700 is arranged between the rear end surface of the second thrust flat bearing 92 and the front end surface of the circular plate 25. However, the annular spacer 700 is disposed in the front end surface of the first thrust flat bearing 91. And the rear end surface of the inner block 23.

[0040]

As described above, in the present invention, the axial movement restricting mechanism for restricting the axial movement of the drive mechanism is provided, and the axial movement restricting mechanism extends from the outer surface of the main shaft in the radial direction. Since it includes an annular flange disposed between the axial end surface of the internal block and the axial end surface of the internal element, and a spacer detachably disposed between the annular flange and the internal element, various types can be prepared in advance. Prepare a spacer with a thickness of 1 mm, and measure the axial distance between the axial end surface of the internal block and the axial end surface of the internal element, and the thickness of the annular flange, etc., prior to assembly of the scroll fluid machine. However, by selecting the spacer with the optimum thickness based on these measurement results, the axial gap between the annular flange and the axial end surface of the internal block, and between the annular flange and the axial end surface of the internal element. Axial direction Between it can be set to a small value. As a result, unpleasant noise and abnormal wear caused by the collision at the contact surface between the main shaft and the internal element adjacent to the main shaft in the axial direction are sufficiently reduced, and the durability of the scroll fluid machine is improved. .

Further, in the present invention, an axial movement restricting mechanism for restricting axial movement of the drive mechanism is provided,
The axial movement restriction mechanism extends in the radial direction from the outer surface of the main shaft, and is disposed between the axial end surface of the internal block and the axial end surface of the internal element, and the annular flange, the annular flange and the internal block. Since spacers that are removably disposed are included between the spacers, spacers of various thicknesses are prepared in advance, and the axial end faces of the internal blocks and the axial direction of the internal elements are arranged before the scroll fluid machine is assembled. By measuring the axial distance to the end face, the thickness of the annular flange, etc., and selecting the spacer with the optimum thickness based on these measurement results, the distance between the annular flange and the axial end face of the inner block can be The axial clearance and the axial clearance between the annular flange and the axial end surface of the internal element can be set to very small values. As a result, unpleasant noise and abnormal wear caused by the collision at the contact surface between the main shaft and the internal element adjacent to the main shaft in the axial direction are sufficiently reduced, and the durability of the scroll fluid machine is improved. .

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a scroll type fluid machine according to a conventional technique.

FIG. 2 is a partially enlarged sectional view of the scroll type fluid machine shown in FIG.

3 is an enlarged cross-sectional view of a thrust plane bearing of the scroll fluid machine of FIG.

FIG. 4 is a partially enlarged sectional view of a radial plane bearing of the scroll type fluid machine shown in FIG.

FIG. 5 is a partially enlarged sectional view of the scroll type fluid machine according to the first embodiment of the present invention.

FIG. 6 is a sectional view of a scroll type fluid machine according to a second embodiment of the present invention.

7 is a partially enlarged sectional view of the scroll type fluid machine shown in FIG.

[Explanation of symbols]

 300 Compressor 310 Housing 311 Front end plate 312 Casing 314 Main shaft 314c Annular flange 320 Inner block 326 1st thrust plane bearing 327 2nd thrust plane bearing 330 Fixed scroll 340 Movable scroll 350 Rotation prevention mechanism 400 Annular spacer 10 Compressor 20 Scroll type Fluid compression mechanism 21 Fixed scroll 22 Movable scroll 23 Inner block 30 Drive mechanism 31 Main shaft 31c Annular flange 32 Motor 91 First thrust plane bearing 92 Second thrust plane bearing 700 Annular spacer

Claims (14)

[Claims] A fixed scroll having a housing, a first end plate and a first spiral body extending from the first end plate; and a second end arranged in the housing. A movable scroll having a plate and a second spiral body extending from the second end plate, wherein the first spiral body and the second spiral body are fitted with offset in the circumferential direction and the radial direction, A main shaft forming a plurality of line contacts defining at least a pair of sealed fluid pockets and further axially disposed within the housing and operatively coupled to the orbiting scroll for revolving the orbiting scroll. A drive mechanism having: an inner block fixed in the housing to rotatably support a part of the main shaft; and arranged in the housing and at an axial distance from the inner block. An internal element provided, a rotation preventing mechanism that is connected to the movable scroll, prevents the movable scroll from rotating when the movable scroll revolves, and reduces the volume of the fluid pocket; An axial movement restricting mechanism for restricting axial movement, wherein the axial movement restricting mechanism extends in a radial direction from an outer surface of the main shaft, and has an axial end surface of the internal block and an axial end surface of the internal element. A scroll-type fluid machine, comprising: an annular flange disposed between the annular flange and a spacer detachably disposed between the annular flange and the internal element. 2. The axial movement restricting mechanism further includes a first thrust flat bearing disposed between the annular flange and an axial end surface of the inner block, and between the annular flange and the spacer. The scroll type fluid machine according to claim 1, further comprising a second thrust plane bearing disposed in the. 3. The scroll type fluid machine according to claim 1, wherein the spacer is made of steel. 4. The first thrust plane bearing has a first annular element made of steel and a second annular element made of phosphor bronze, and the second annular element is provided on an end surface of the first annular element. Is arranged,
The scroll fluid machine according to claim 2 or 3, wherein an end surface of the second annular element faces the annular flange. 5. The axial movement restricting mechanism is arranged at least partially in an oil passage defined by the spindle and the internal block. 2. A scroll type fluid machine according to item 1. 6. The scroll type fluid machine according to claim 1, wherein the housing houses the drive mechanism in an airtight manner. 7. The scroll type fluid machine according to claim 1, wherein the drive mechanism further includes a motor that is connected to the main shaft and rotates the main shaft. 8. A fixed scroll having a housing, having a first end plate and a first spiral body extending from the first end plate, the fixed scroll being provided in the housing, and having a second end. A movable scroll having a plate and a second spiral body extending from the second end plate, wherein the first spiral body and the second spiral body are fitted with offset in the circumferential direction and the radial direction, A main shaft forming a plurality of line contacts defining at least a pair of sealed fluid pockets and further axially disposed within the housing and operatively coupled to the orbiting scroll for revolving the orbiting scroll. A drive mechanism having: an inner block fixed in the housing to rotatably support a part of the main shaft; and arranged in the housing and at an axial distance from the inner block. An internal element provided, a rotation preventing mechanism that is connected to the movable scroll, prevents the movable scroll from rotating when the movable scroll revolves, and reduces the volume of the fluid pocket; An axial movement restricting mechanism for restricting axial movement, wherein the axial movement restricting mechanism extends in a radial direction from an outer surface of the main shaft, and has an axial end surface of the internal block and an axial end surface of the internal element. A scroll-type fluid machine, comprising: an annular flange disposed between the annular flange and a spacer detachably disposed between the annular flange and the internal block. 9. The axial movement restricting mechanism further includes a first thrust flat bearing disposed between the annular flange and an axial end surface of the inner element, and between the annular flange and the spacer. 9. The scroll type fluid machine according to claim 8, further comprising a second thrust plane bearing disposed in the scroll type fluid machine. 10. The scroll type fluid machine according to claim 8, wherein the spacer is made of steel. 11. The first thrust plane bearing has a first annular element made of steel and a second annular element made of phosphor bronze, and the second annular element is provided on an end surface of the first annular element. 11. The scroll type fluid machine according to claim 9, wherein the scroll type fluid machine is arranged, and an end surface of the second annular element faces the annular flange. 12. The axial movement restricting mechanism is arranged at least partially in an oil passage defined by the main shaft and the inner block.
12. The scroll type fluid machine according to any one of 1 to 11. 13. The scroll type fluid machine according to claim 8, wherein the housing houses the drive mechanism in an airtight manner. 14. The scroll type fluid machine according to claim 8, wherein the drive mechanism further includes a motor that is connected to the main shaft and rotates the main shaft.