JP2800300B2 - Scroll compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a scroll compressor, and is effective when used as, for example, a refrigerant compressor for an air conditioner for an automobile.

[Conventional technology and its problems]

In the conventional scroll compressor, as shown in FIG. 9, the axial length of the movable scroll 100 and the fixed scroll 101 cannot be increased, and therefore, in order to obtain a predetermined discharge capacity, both the scrolls 100 and 101 are required. Had to be enlarged in the radial direction. As a result, the outer diameter of the entire scroll compressor becomes large, and therefore, particularly when used as a refrigerant compressor of an air conditioner for an automobile, there is a problem that the mountability in an engine room is deteriorated.
The problem of the conventional scroll compressor will be further described below.

As shown in FIG. 9, when revolving the orbiting scroll 100 in a predetermined direction, the orbiting must be performed while compressing the refrigerant in the working chamber 102, and therefore, the reaction force F ₁ required for compression.
Will be added to the movable scroll 100. In other words, the shaft 103 is a reaction force applied to the movable scroll 100.
At the force F ₂ corresponding to F ₁ must be displaced to the movable scroll 100. Here, the reaction force F ₁ and the driving force F ₂ for the operating direction are different, so that the direction of the moment for rotating the movable scroll 100 is generated. This rotational moment is offset by the moment generated by the reaction forces X ₁ and X ₂ applied to the thrust support portions 104 and 105. Here, the sum of the thrust reaction forces X ₁ and X ₂ is equal to the pressing force X ₃ by which the refrigerant in the working chamber 102 presses the movable scroll 100. Meanwhile, if the order pressing force X ₃ is made substantially constant by the volume of the working chamber 102, too becomes a moment due to the reaction force F ₁ and the driving force F ₂ is increased (Fig. 10 shown), the supporting force X _1, X
_The moment by ₂ must be equal to it. Therefore, as shown in FIG. 10, a force for pressing the movable scroll 100 toward the support member 105 cannot be generated. As a result the movable scroll 100 is in contact with the fixed scroll 101 side, so that the reaction force X ₂ occurs at that site. In other words, the support member 105 is separated from the support plate 106.

If the movable scroll 100 starts revolving while being in contact with the fixed scroll 101, the contact surface pressure between the movable scroll 100 and the fixed scroll 101 increases, and the driving force required for rotating the movable scroll 100 decreases. Not only does it become unnecessarily large, but also the durability of the movable scroll and the fixed scroll 101 deteriorates. Furthermore, as a result of the movable scroll 100 being inclined, there is a possibility that leakage may occur between the movable scroll 100 and the fixed scroll 101.

For the reasons stated above, it is not possible to design the movable scroll 100 and the fixed scroll 101 in a shape such as a moment due to the reaction force F ₁ and the driving force F ₂ becomes excessive, the width of the result as the movable scroll and the fixed scroll It had to be small.

[Problems to be solved by the invention]

The present invention has been devised in view of the above points, and has as its object to prevent the movable scroll from coming into contact with the fixed scroll even if the axial width of the movable scroll and the fixed scroll is increased.

[Configuration and operation]

In order to achieve the above object, the scroll compressor according to the present invention includes a thrust support that engages with the movable scroll. In the thrust support, not only the displacement of the movable scroll away from the fixed scroll, but also the movable scroll is fixed. The displacement in the direction toward the scroll is also restricted. By adopting the above configuration, in the scroll compressor of the present invention, the movable scroll is always moved in the axial direction regardless of the magnitude of the compression reaction force applied to the movable scroll and the driving force for driving the movable scroll. It can be held in place. Therefore, in the scroll compressor of the present invention, it is possible to prevent the movable scroll from contacting the fixed scroll with a large surface pressure.

〔The invention's effect〕

In the scroll compressor of the present invention, by providing the above-described thrust support portion, the magnitude of the compression reaction force applied to the orbiting scroll and the magnitude of the bending moment generated by the compression reaction force and the driving force can be freely designed. Can be. Therefore, in the scroll compressor of the present invention, the axial widths of the movable scroll and the fixed scroll can be freely set, which has the effect of increasing the degree of freedom in design. Further, when the axial width of the movable scroll and the fixed scroll is set to be large, the radial length of the movable scroll and the fixed scroll can be reduced,
As a result, the diameter of the entire scroll compressor can be reduced.

Further, in the scroll compressor according to the present invention, the axial displacement of the movable scroll is accurately held by the thrust support portion, so that the fixed scroll can be displaced in the axial direction. When the axial displacement of the fixed scroll is permitted as described above, the discharge action of the compressor can be limited by displacing the fixed scroll.
In such a case, it is possible to reduce the load at the time of starting the compressor.

〔Example〕

Hereinafter, an embodiment of the compressor of the present invention will be described with reference to the drawings. In FIG. 1, reference numeral 200 denotes a front housing made of an aluminum alloy, which has stepped cylindrical portions 201 and 202, and which holds bearings 203 and 204. The small diameter portion of the shaft 103 is rotatably supported by the bearing 204, and the large diameter portion 11 of the shaft 103 is supported by the bearing 203.
0 is rotatably supported. The shaft 103 is a medium diameter part 11
The shaft 103 that prevents refrigerant and lubricating oil inside the compressor from leaking to the outside along the shaft 103 by a shaft seal 205 disposed around the middle diameter portion 111.
Is integrally formed with a crank portion 114. The crank portion 114 is disposed eccentrically from the rotation axis of the shaft 103 by a predetermined amount. The shaft 103 has a movable scroll 100
The balance weight 112 is fixed so as to compensate for the eccentricity.

The movable scroll 100 has a bearing 210 on the crank 114
Are rotatably engaged with each other. Therefore, the crank part 11
In response to the rotation of 4, the movable scroll 100 is moved to the rear housing 21.
It will revolve within 1. The fixed scroll 101 is fixed to the rear housing 211 via bolts 212. In addition, a suction port 213 and a discharge port 214 are opened in the rear housing 211. The fixed scroll 101 is defined between the suction port 213 and the discharge port 214. In FIG. 11, the left space of the fixed scroll 101 is a suction pressure space, and the right space of the fixed scroll 101 is a discharge pressure space. A discharge valve 215 is fixed to the fixed scroll 101 together with a valve cover 216 by bolts 217.

A thrust support plate 220 is sandwiched between the front housing 200 and the rear housing 211. Movable scroll 1
Of the 00, the surface facing the thrust support plate 220 is the first
A support plate forming the support surface 221 is mounted. This support plate and the aforementioned thrust support plate 220
Are both made of bearing steel. On the other hand, a support member 222 is attached and fixed to the movable scroll 100 by a circlip 226 so as to sandwich the thrust support plate 220 together with the first support surface.

A ball 223 is held between the first support surface and a fixed support surface formed on the thrust support plate 220. Also, a second support surface 224 formed on the support member 222 and a thrust support plate
A ball 225 is arranged between the fixed support surface 220 and the ball 220. Therefore, the first support surface 221, the ball 223, the thrust support plate
The axial displacement of the orbiting scroll 100 is regulated by the 220, the ball 225 and the second support surface 224.

The balls 223 and 225 are held by a rotation prevention regulating plate 230 as shown in FIG. The anti-rotation control plate 230 includes a pair of plate members for holding the ball 223 (225), and each plate member has a holding hole 231 having a diameter corresponding to the revolution radius of the movable scroll 200.

Next, the operation of the compressor having the above configuration will be described. The rotational driving force of the vehicle running engine is transmitted to the shaft 103 via an electromagnetic clutch (not shown) provided on the outer surface of the cylindrical portion 202 of the front housing. Under the driving force, the shaft 103 rotates in the housing 200 around the rotation axis. Here, since the crank portion 111 is eccentric with respect to the rotation axis of the shaft 103 by a predetermined amount, the movable scroll revolves in the housing 211. At this time, the rotation of the movable scroll 100 is caused by rotation control plate 230 and ball.
Prevented by engagement with 225 and 223.

FIGS. 3A to 3D show the revolving motion of the movable scroll 100. FIG. With this revolving motion, the movable scroll 10
The working chamber 102 formed between 0 and the fixed scroll 101 increases or decreases its volume. Movable scroll 101
Is a suction pressure space, refrigerant is sucked into the working chamber 102 from the space 150 between the orbiting scroll 100 and the fixed scroll. Next, when the volume of the working chamber 102 is reduced and the refrigerant is compressed and the compressed refrigerant becomes higher than a predetermined pressure, the discharge valve 151 is pushed open from the discharge port 151 to open the discharge chamber 15.
Discharged to 2. In the compressor of this example, the compressor is completed when the orbiting scroll 100 rotates about 2.2 times. The high-pressure refrigerant discharged into the discharge chamber 152 is discharged from the discharge communication hole 214 to the condenser side (not shown) of the refrigeration cycle.

Compression of the refrigerant in the working chamber 102 is applied to the movable scroll 100 as the compression reaction force F _1. Driving force F ₂ corresponding to the reaction force F ₁ will be generated in the crank portion 111 as shown in Figure 4. Since the compressor of this embodiment Aru the axial width of the movable scroll 100 and the fixed scroll 101 to set relatively large as about 35 mm, the bending moment caused by the reaction forces F ₁ and the driving force F ₂ becomes large. This bending moment is the thrust force applied between the fixed support surface 228 of the thrust support plate and the first support surface 221 of the movable scroll 100.
X ₁ , and the thrust force generated between the fixed support surface 229 of the thrust support plate 220 and the second support surface 224 of the orbiting scroll 100
It would be received by X _2. In addition, thrust force X ₁
The sum of X ₂ is equal to the thrust force X ₃ applied to the movable scroll 100 from working chamber 102.

In this example, the first support surface 221, the ball 223, and the thrust support plate 22
0, the thrust support portion by the ball 225 and the second support surface 224
240 are formed. In the present example, the axial displacement of the orbiting scroll 100 is accurately regulated in both directions by the thrust support portion 240. That is, the thrust support portion 240 regulates not only the direction in which the movable scroll 100 moves away from the fixed scroll 101, but also the displacement of the movable scroll 100 in the direction toward the fixed scroll 101. Therefore, the compressor of this example
Even would F ₁ and the driving force moment any size resulting from F _2, not inclining the movable scroll 100. As a result, in the present example, as described above, the axial width of the movable scroll 100 and the fixed scroll 101 is set to 35
mm can be set relatively large. As a result, the radial length of the movable scroll 100 and the fixed scroll 101 can be reduced, and the outer diameters of the housings 200 and 211 can be reduced to about 105 mm.

In the above example, the first support surface 221 and the second support surface 2
The thrust support plate 220 is arranged between the movable scroll 100 side and the thrust support plate 220 therebetween. However, as shown in FIG. The first support surface 321 and the second support surface 32 are fixed to a boss 600 protruding from an end plate of the scroll 100.
2 may be fixed to the housing 211 side.

Further, in the above example, the rotation restricting plate 2 is attached to the thrust support 240.
Although the thrust support and the rotation prevention are achieved at the same time by disposing 30, the functions of the thrust support and the rotation prevention may be separately provided. FIG. 6 shows the embodiment. In this embodiment, the thrust support plate 420 is sandwiched between the housing 200 and the rear housing 211.
Then, the first support surface 221 that is in sliding contact with the thrust support plate is formed on the movable scroll 100. Thrust support plate 420
A support member 421 having a second support surface 224 that is in sliding contact with the movable scroll is fixed to the movable scroll. Further, a movable joint 430 is provided separately from the thrust support portion 240, and the movable joint 100 prevents the movable scroll 100 from rotating.

Here, the appearance of the movable joint 430 is shown in FIG. Movable joint 4
One of the fixing plates 431 is fixed in the housing 200.
Although not shown in FIG. 7, the other fixed plate is fixed to the movable scroll 100 as a thrust support plate 421 in FIG.

The movable joint 430 is provided between the two fixed plates. The engagement of these members 431, 431 and 421 prevents the movable scroll 100 from rotating.

FIG. 8 shows still another embodiment of the present invention. In the present invention, since the above-described thrust support portion 240 is provided, the axial displacement of the movable scroll 100 is surely restricted both in the direction toward the fixed scroll 101 and in the direction away from the fixed scroll 101. In other words,
In the present embodiment, the provision of the thrust support portion 240 eliminates the occurrence of the situation where the movable scroll is held by the engagement between the fixed scroll 101 and the movable scroll 100. Thus, in the embodiment shown in FIG. 8, the fixed scroll is disposed so as to be displaceable in the axial direction. That is, the sliding support portion 500 is integrally formed with the fixed scroll 101,
The sliding support portion 500 is connected to the support surface 50 of the inner surface of the rear housing 211.
It is slid in contact with 1. Note that a discharge chamber 152 is formed inside the rear housing 211, and a holding spring 502 is disposed in the discharge chamber 152. The holding spring 502 presses the fixed scroll 101 toward the movable scroll 100 with a relatively weak set pressure.

8, a locking wall 506 is formed between the center housing 505 and the rear housing 211.
6, the fixed scroll 101 is held. In addition,
The force for pressing the fixed scroll 101 toward the locking wall 506 is the above-described holding force of the holding spring 502 and the pressure difference between the front and rear of the fixed scroll 101. In other words, the high pressure of the discharge pressure chamber 152 is applied to the right side of the fixed scroll 101 in the figure, and the pressure of the working chamber 102 is applied to the left side of the fixed scroll 101 in the figure. The pressure in the working chamber 102 fluctuates from the suction pressure to the discharge pressure, and its integral value is smaller than the discharge pressure. Therefore, the differential pressure pushes the fixed scroll 101 toward the locking wall 506 side. Therefore, the position of the fixed scroll 101 does not change during normal operation.

The axial displacement of the fixed scroll 101 is performed by switching the control valve 550. The control valve 550 is switched between a state where the discharge passage 551 is opened as shown in FIG. 8 and a state where the discharge passage 551 is closed and the discharge passage 551 and the suction passage 552 are communicated. In the state shown in FIG. 8, the discharge passage 551 is open, and the scroll compressor performs the normal compression discharge.

On the other hand, when the position of the control valve 550 is switched and the discharge passage 551 and the suction passage 552 are communicated, the pressure in the discharge chamber 152 is released to the suction passage 552 side, and as a result, the pressure in the discharge chamber 152 is sucked. Pressure. In this state, the fixed scroll 101
Is reduced in the leftward direction in FIG.
Therefore, the refrigerant pressure in the working chamber 102 overcomes the pressure in the discharge chamber 152, and the fixed scroll 101 can be displaced rightward in FIG. Here, if the fixed scroll 101 fluctuates, the gap between the fixed scroll 101 and the movable scroll 100 increases, and the working chamber 10
2 will not be able to retain its shape. This means that the refrigerant cannot be compressed and discharged depending on the working chamber 102.

Therefore, in an abnormal time when the discharge pressure of the compressor is particularly high or the discharge refrigerant temperature is particularly high, the operation of the compressor can be stopped by switching the control valve 550. Further, conventionally, if the cooling capacity is adjusted even when the electromagnetic clutch is intermittent, if the control valve 550 is used instead of switching, the impact noise generated when the electromagnetic clutch is intermittently not only disappears, but also the durability of the electromagnetic clutch is reduced. Can be greatly improved.

FIG. 11 shows still another embodiment of the compressor of the present invention. The embodiment shown in FIG. 11 is a combination of the compressor having the above structure and a load adjusting mechanism.

That is, the plate 601 supporting the ball 225 is
The support member 222 is disposed on the hub portion of the movable scroll 100 so as to be axially displaceable. The positioning of the support member 222 in the axial direction is performed by screwing the nut 602 into a screw portion formed on the hub portion of the movable scroll 100.

With the above configuration, by adjusting the position of the nut 602, the pressing force applied to the ball 225 can be adjusted, and the movable scroll 100 can be stably supported with an appropriate pressing force. That is, when the nut 602 is tightened, the plate 601 is elastically deformed depending on the degree of the tightening, and the movable scroll 100 is stably supported by the thrust support plate 220 by the load caused by the elastic deformation.

[Brief description of the drawings]

1 is a sectional view showing an embodiment of the compressor of the present invention, FIG. 2 is a perspective view showing a rotation restricting plate shown in FIG. 1, and FIGS. 3 (a) and 3 (b) are compressors shown in FIG. FIG. 4 is an explanatory view showing a compressor reaction force and a driving force of the compressor shown in FIG. 1; FIG. 5 is a cross-sectional view showing another example of the compressor of the present invention; FIG. 6 is a sectional view showing still another example of the compressor of the present invention, FIG. 7 is a perspective view showing a movable joint portion of the compressor shown in FIG. 6, and FIG. 8 is still another example of the compressor of the present invention. 9 and 10 are explanatory views illustrating a compression reaction force and a driving force in a compressor using a conventional thrust support, and FIG. 11 is another example of the compressor of the present invention. FIG. 100 …… Movable scroll, 101 …… Fixed scroll, 102…
… Working chamber, 103 …… Shaft, 111 …… Crank chamber, 220 ……
Thrust support plate, 221 ... first support surface, 223 ... ball, 224
... Second support surface, 225 ball, 240 thrust support portion.

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-60-101285 (JP, A) JP-A-57-173586 (JP, A) Actually open 1987-173577 (JP, U) Actually open 1983 8782 (JP, U) Japanese Utility Model Showa 62-116187 (JP, U) Japanese Utility Model Showa 63-136281 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18/02 311 F04C 29/10 331

Claims (8)

(57) [Claims] A shaft having a crank portion which is rotated by receiving a rotational force and is eccentric with respect to a rotation shaft by a predetermined amount, rotatably engaged with the crank portion, and provided around a rotation axis of the shaft. A movable scroll that performs a revolving motion; a fixed scroll that engages with the movable scroll to form an operating chamber together with the movable scroll; a direction in which the movable scroll is engaged with the movable scroll and moves toward the fixed scroll; and the movable scroll. Is a scroll compressor having a thrust support portion that regulates displacement in both directions away from the fixed scroll, wherein the thrust support portion includes a first support surface and a second support disposed on the movable scroll side. And a fixed support surface fixedly disposed between the first support surface and the second support surface. When the scroll is displaced to the fixed scroll side, the displacement is regulated by the engagement between the fixed support surface and the second support surface, and when the movable scroll is displaced away from the fixed scroll, A scroll compressor characterized in that the displacement is regulated by the fixed support surface and the first support surface. 2. A shaft having a crank portion which is rotated by receiving a rotational force and is decentered by a predetermined amount with respect to a rotation axis, rotatably engages with the crank portion, and rotates around a rotation axis of the shaft. A movable scroll that performs a revolving motion; a fixed scroll that engages with the movable scroll to form an operating chamber together with the movable scroll; a direction in which the movable scroll is engaged with the movable scroll and moves toward the fixed scroll; and the movable scroll. Is a scroll compressor having a thrust support portion that regulates displacement in both directions away from the fixed scroll, wherein the thrust support portion is an end plate of the movable scroll to receive rotational driving force from the crank portion. A support surface disposed on a boss projecting from the movable scroll and integrally displaced with the movable scroll; It has a first fixed support surface and a second fixed support surface fixedly arranged to hold the support surface from both sides. When the movable scroll is displaced in a direction away from the fixed scroll, the support surface and the second fixed support surface are fixed to each other. When the movable scroll is displaced in the direction toward the fixed scroll side, the support surface and the second fixed support surface are engaged with each other when the movable scroll is displaced in the direction toward the fixed scroll. The displacement is regulated, and the thrust support portion interposes a ball between the support surface and the first fixed support surface and between the support surface and the second fixed support surface. A scroll compressor characterized by the following. 3. The thrust support portion has a ball interposed between the support surface and the first fixed support surface and between the support surface and the second fixed support surface. 2. The scroll compressor according to 1. 4. The scroll compressor according to claim 2, wherein said ball is held by a rotation preventing plate. 5. A shaft having a crank portion which is rotated by receiving a rotational force and is decentered by a predetermined amount with respect to a rotation axis, rotatably engages with the crank portion, and rotates around a rotation axis of the shaft. A movable scroll that performs a revolving motion; a fixed scroll that engages with the movable scroll to form an operating chamber together with the movable scroll; a direction in which the movable scroll is engaged with the movable scroll and moves toward the fixed scroll; and the movable scroll. Is a scroll compressor having a thrust support portion that regulates displacement in both directions away from the fixed scroll, wherein the fixed scroll is formed at a position facing the movable scroll, and the fixed scroll is Facing the movable scroll in a direction away from the movable scroll The fixed scroll is pressed and held on the movable scroll side by pressing means provided on a portion of the fixed scroll opposite to the movable scroll, The fluid compressed in the working chamber is discharged to a portion of the fixed scroll opposite to the movable scroll, and the fluid is sucked into a portion of the fixed scroll opposite to the movable scroll and to the working chamber. A scroll-type compressor provided with an on-off valve that communicates with a suction passage for introducing fluid to be supplied and that opens and closes the communication. 6. The fixed scroll is held so as to be displaceable in a direction away from the movable scroll, and the fixed scroll is pressed and held on the movable scroll side by a pressing means. 2. The scroll compressor according to 2. 7. The scroll type compressor according to claim 5, wherein said pressing means comprises a spring disposed on a surface of said fixed scroll opposite to said movable scroll. 8. A shaft having a crank portion which is rotated by receiving a rotational force and is decentered by a predetermined amount with respect to a rotating shaft, rotatably engages with the crank portion, and rotates around a rotating shaft of the shaft. A movable scroll that performs a revolving motion; a fixed scroll that engages with the movable scroll to form a working chamber together with the movable scroll; a direction in which the movable scroll engages with the movable scroll, and a direction toward the fixed scroll, and the movable scroll. A scroll-type compressor including a thrust support portion that regulates displacement in both directions away from the fixed scroll, wherein the thrust support portion is displaced integrally with the movable scroll; And a fixed-side support surface disposed to engage with the movable-side support surface and the fixed-side support surface. Surface and the scroll type compressor, wherein a relative position therebetween is disposed adjustably in.