JPS6111494A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To increase the gas circulation amount per hour by installing a means for increasing the thermal resistance between the passage for the low-pressure gas inhaled into a compression mechanism and a driving motor into a sealed case and eliminating the bad influence of the motor for the low-pressure gas. CONSTITUTION:The opening port 111a at the part positioned in the sealed case 11 of a suction pipe 111 is set close to a suction port of a scroll type compression mechanism 150, namely to a hole 58 formed onto a frame 14. Therefore, a even if a motor 16 generates heat during operation, the calorific heat which the low-pressure gas receives from the motor 16 side during the movement to the hole 58 through the suction pipe 111 is exceedingly small. Since the opening port 111a is set close to the hole 58, the thermal resistance between the motor 16 and a low-pressure gas passage can be increased sufficiently. Therefore, the scroll type compression mechanism 15 can always inhale the low-pressure gas having a low temperature which does not receive the influence of the heat generated by the motor 16, and the gas circulation amount per hour can be increased markedly, and the performance can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to an improvement of a scroll-type compression device comprising a Sufu'coal-type compression mechanism housed in a closed case.

[Technical Problems with the Invention] A scroll-type compression device has been known as a low-pressure compression device. This compression device has a compression mechanism constructed by combining a pair of scroll blades in the axial direction, and has advantages such as small size, high efficiency, and low vibration.

By the way, this 41) Sufu ``L-le desire compression Urooka IJ.''

Usually, a frame lz is fixed at a slightly upper position inside the sealed case in a form that partitions the inside of the sealed case in the vertical direction, and a scroll type compression mechanism is arranged below this frame. A motor is disposed to provide driving power to the scroll type compression mechanism, and lubricating oil is housed in the bottom of the sealed case. A scroll-type compression mechanism usually includes a fixed element having a protruding scroll blade, and a movable element disposed below the fixed element and having a protruding scroll blade that meshes with the scroll blade. A bearing hole is provided vertically through the frame, and the rotating shaft of the motor described above is rotatably supported by the bearing hole.

Further, an eccentric coupling mechanism and an Oldham mechanism are provided between the upper end of the rotating shaft and the movable element, and the eccentric coupling mechanism and Oldham mechanism cause the movable element to perform a turning motion without rotation. In a scroll-type compression device configured in this way, the lower surface of the movable element is normally placed in a low-pressure atmosphere and fixed in order to use the space where the motor is installed as a gas-liquid separator. A flow path IM configuration is adopted in which the upper surface side of the element is in a high-pressure atmosphere.

However, the conventional scroll type compression device configured as described above has the following problems. That is, since the inside of the sealed case is used as a gas-liquid separator, low-pressure gas is once sucked into the scroll-type compression mechanism through the space inside the sealed case that communicates with the space where the motor is installed. The motor generates heat during operation.

Therefore, the low-pressure gas sucked into the scroll-type compression mechanism is heated by the heat generated by the motor, and as a result, the low-pressure gas with an increased specific volume is sucked into the scroll-type compression mechanism. There was a problem that the performance could not be improved that much.

[Objective of the Invention 1 The present invention has been made in view of the above circumstances, and its purpose is to provide a scroll-type compression system which operates with a low pressure atmosphere on the lower surface side of the movable element. To provide a scroll type compression device which can prevent low-pressure gas sucked laterally from being heated by heat generated by a motor, thereby improving the performance of the compression device.

[Summary of the Invention] The present invention is characterized in that means for increasing the thermal resistance between the flow path of the low-pressure gas sucked into the scroll-type compression mechanism and the drive motor is provided in the closed case.

[Effects of the Invention] With the above configuration, the low-pressure gas sucked into the scroll type compression mechanism is sucked in without being affected by the heat of the motor, that is, without increasing the temperature. Therefore, compared to the conventional system, the gas circulation l per unit time can be significantly increased, and the performance can be improved.

[Embodiments of the invention] Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, reference numeral 11 indicates a vertically long sealed case, and this sealed case 11 is a cylindrical intermediate case 1.
2, and closing cases 13a, 13b, etc., which are welded with J to close both ends of this intermediate case 120. A frame 14 is provided at an upper position inside the sealed case 11 in a form that partitions the inside of the sealed case 11 in the vertical direction.
is fixed. A scroll compressor 11115 is arranged above the frame 14, and a scroll compressor 11115 is arranged above the frame 14.
A motor 16 for providing driving power to the scroll compression mechanism 15 is disposed below the scroll compression mechanism 15, and a lubricating oil 17 is housed in the bottom of the sealed case 11.

The scroll type compression mechanism 15 is composed of a fixed element 21 and a movable element 22 arranged below the fixed element 21, as in the known one.

The fixing element 21 includes a disk-shaped mirror plate 23, an annular wall 24 protruding from the peripheral edge of one surface of the mirror plate 23, and the annular wall 2.
4, a scroll 125 protrudes at a height approximately equal to that of the annular wall 24, and a discharge port 26 provided approximately at the center of the end plate 23.
The inner edge of the annular shape 24 is formed into a notch 27 such as a curved surface having a curvature of ii1 to 1z or a tapered surface as shown in FIGS. 2(a) and (1). As above 1. The fixing element 21 has two structures, with the annular wall 24 and the scroll blades 25 projecting downward.
The peripheral edge of the frame 14 is hermetically fixed to the peripheral edge of the upper surface of the frame 14 by bolts 28. In addition, when fixing, fixing element 2
A cap 29 is applied to the top surface of 1, and this cap 2
9 is also integrally fixed by the bolt 28. A gap 3 of a predetermined thickness is formed between the cap 29 and the top surface of the end plate 23.
This gap 30
A hole 31 is formed in a part of the wall forming the hole. Also,
A hole 32 for guiding lubricating oil, which will be described later, is formed in a part of the side wall. On the other hand, the movable element 22 includes a mirror plate 33 having an outer diameter slightly larger than the inner diameter of the annular wall 24, and a scroll blade 34 protruding from one surface of the mirror plate 33 at a height approximately equal to the height of the scroll blade 25. and a cylindrical portion 35 protruding from the other central portion of the end plate 33.

The peripheral edge of the mirror lff 133 on the side where the scroll blades 34 protrude is shown in FIGS. 3(a) and 3(b).
JJ: Formed on a cutout surface 36 such as a sea urchin tapered surface. The movable element 22 configured as described above is
The scroll blades 34 and the scroll blades 25 are engaged with each other with the protruding direction of the scroll blades 34 being 1 point upward, and the peripheral portion of the mirror plate 33 and the end face of the annular wall 24 and the end face of the scroll blades 34, the mirror plate 23, and the scroll are in mesh with each other. wing 25
The end face of the end face and the end plate 33 are installed so that they are in sliding contact with each other,
This mounted state is maintained by an Oldham mechanism 40 provided between the mirror plate 33 and the frame 14.

The Oldham mechanism 40 includes key grooves 418 and 41b provided at two locations on the same line drawn through the center of the end plate 33 at the lower peripheral edge of the end plate 33, and the key grooves 41a, 41b,
11b, and on a line perpendicular to the arrangement direction of frame 14.
A key groove 428 provided on the top surface of the
42b and the key m4 on one side as shown in FIG.
The ring 45 has keys 43a and 43'b that fit into the key grooves 1a and 41b, and keys 44a and 44b that fit into the key grooves 42a and 42b on the other side. On both sides of the ring 45, for example, mesh-like oil grooves 46 are actually formed to reduce sliding resistance, as shown in FIG. Further, each of the key grooves 42a, 42b.

On the inner surfaces of the bottles 41a and 41b, a stepped portion 47 for reducing the sliding area with the key is formed, as represented by the key groove 42b in FIG.

A bearing hole 51 eccentric to the axis of the cylindrical portion 35 of the movable element 22 is provided through the frame 14 in the vertical direction, and the bearing hole 51 is located on the cylindrical portion 35 side of the bearing hole 51. The part is formed to have a large diameter. The frame structure on the larger diameter side is specifically constructed as shown in FIG. That is, the outermost part has an outer diameter that is approximately equal to the inner diameter of the sealed case 11, and the inner diameter is the same as that of the annular wall 2.
An annular wall 52 is formed to which the annular wall 24 is fixed by tightening L1 with a bolt 28, and the annular wall 52 is larger than the inner diameter of the ring 45.
An annular receiver 56 is formed inside of the annular receiver 56, which is further lowered by one step and receives a thrust force reduction tllR59, which will be described later. The surface of the 8-receiver is divided into a plurality of parts in the circumferential direction by grooves 57 provided radially, and at least one of the grooves 57 is connected to the frame 1.
The hole 5 is provided in the wall of 4 and communicates directly with the hole 5 through which the inner part i directly communicates. Note that the keys 11142a and 42b are formed on a receiving surface 55.

Specifically, as shown in FIG. 7, the main parts of the thrust saw reduction mechanism 59 include an annular body 60 that is fitted into and supported by the surface 56, and is carved on the upper surface of the annular body 60. An annular groove 61, and an inner seal ring 62 and an outer seal made of, for example, Eblete tetrafluoride, which are attached to the annular groove 61 and which are in close contact with the inner and outer surfaces of the annular groove 61 and partially protrude outward, respectively. ring 63, and a ring-shaped ring which is inserted between the lower surfaces of these inner and outer seal rings 62 and 63 and the bottom wall of the annular groove 61 and applies a force in the direction of upward protrusion to the inner and outer seal rings 62 and 63. It is composed of a leaf spring 64. Inside the mirror plate 33, with the thrust force reduction mechanism 59 mounted as shown in FIG.
Holes 65 and 66 that allow the annular space Q surrounded by the lower surface of the end plate 33 to always communicate with the medium pressure boats s and s' of the compression chamber P.
is formed.

A rotating shaft 70 of the motor 16 is rotatably supported in the bearing hole 51 of the frame 14 .

The rotating shaft 70 has a large diameter portion 71 formed in a portion located in the large diameter portion of the bearing hole 51, and a small shaft 72 that fits into the aforementioned cylindrical portion 35 is protruded from this large diameter portion 71. There is. The rotating shaft 70 has an 8SII lubricant 17 at its lower end.
The lower end portion thereof is supported by a sub-bearing 73 fixed to the inner surface of the sealed case 11.

The sub-bearing 73 is broadly divided into a bearing support member 74 and a sub-bearing main body 75 fixed to the bearing support member 74 so as to be finely adjustable. The bearing support member 74 is formed, for example, by pressing a disc-shaped member or by casting, and the outer diameter of the bearing support member 74 is approximately 2.
Almost equal to the inner diameter of the intermediate case 12 of the sealed case 11,
A peripheral wall 76 having a height greater than the thickness of the member is formed, a relatively large diameter hole 77 is formed in the center, and a peripheral wall 76 is formed between the hole 77 and the peripheral wall 76. A plurality of holes 78 are formed in the direction.

The bearing support member 74 formed as described above is fitted into the lower end of the intermediate case 12 at a position where it is immersed in the lubricating oil 17 with the projecting direction of the projecting peripheral wall 76 facing upward, and in this state, the cylindrical portion 76 is fixed to the intermediate case 12 by spot welding or the like.

On the other hand, the sub-bearing main body 75 includes a cylindrical portion 79 that supports the radial load at the lower end of the rotating shaft 70, and a thrust I-1 that is provided to protrude inward from the lower end of the cylindrical portion 79 and that is applied to the rotating shaft 70.
It is composed of an annular portion 80 that supports part of the load, and a flange portion 81 that projects from the outer periphery of this annular portion 80. The sub-bearing main body 75 configured as described above connects the cylindrical portion 79 to the rotating shaft 7 through the hole 77 provided in the bearing support member 74.
0, and in this state, the flange 81
At 82, the fastening is fixed to the bearing support member 74.

Note that the bolt insertion hole provided in the collar 81 for mounting the bolt 82 is formed to be slightly larger than the outer diameter of the poles 1 to 82, so that the mounting position of the secondary bearing body 75 can be finely adjusted. J: The sea urchin is turning.

Inside the rotating shaft 70, lr! is generated by the action of a centrifugal pump. I lubricant 17
A hole 90 for pumping up the water is formed on the bearing surface or at the fitting portion between the small shaft 72 and the cylindrical portion 35. The shape of the entrance part of this hole 90, that is, the part located at the lower end of the rotating shaft 70, includes a part 91 extending upward from the center of the lower end surface of the rotating shaft 70, and a part 91 extending radially from this part 91 to the cylindrical part. It is a combination of a portion 92 extending to the inner surface of the rotating shaft 79 and a portion 93 extending vertically at the peripheral edge position within the rotating shaft 70 so as to intersect the portion 92 at right angles.

The motor 16 is fixed with the rotor 100 inside.

It is constituted by a squirrel-cage induction motor in which electrons 101 are disposed outside and a stator 101 is fixed to the inner surface of an intermediate case 12.

On the other hand, a ratchet type reversal prevention mechanism 103 is provided between the balance weight 102 protruding from the upper end of the rotor 100 of the motor 16 and the frame 14, and this reversal prevention mechanism 103 has a specific The system is constructed as shown in FIG. That is, balance weight 1
02 is provided with a bottomed hole 105 facing in the rotation axis center line direction, and a rod 10 for the swivel and collar is installed in this bottomed hole 105.
A spring 107 is provided between the rod 106 and the inner surface of the bottom wall of the bottomed hole 105 to apply a force in the direction of protruding the rod 106 from the bottomed hole 105. A claw-shaped notch 108 is provided on the outer surface of the frame 14 to which the tip of the frame 106 is welded.

Furthermore, the scroll type compression v111111
A suction pipe 111 is provided airtightly passing through the space 110 so as to communicate with the space 110. A portion of the suction pipe 111 located within the sealed space 11 extends horizontally in close proximity to the hole 58 to a position passing directly below the hole 58 formed in the frame 14. In a portion of the suction pipe 111 located inside the sealed case 11, an opening 111a is provided opposite to the hole 58, which is formed by cutting this portion diagonally.

Further, a discharge pipe 113 is connected to the wall of the closed case 13a so as to communicate with a space 112 formed between the wall and the fixing element 21.

Note that 114 in FIG. 1 indicates lll! pushed out into the space 112. 1 shows holes provided in the annular wall 24 and the frame 14 for returning lubricating oil below the frame 14;
15 indicates a balance weight, 116 indicates a connection mechanism for power supply to the motor 16, and 117 indicates a hole through which lubricating oil passes.

Next, the operation of the compression device configured as described above will be explained.

First, when power is supplied to the ball 16, the rotating shaft 70 starts rotating. This rotation is smoothly maintained by both the bearing hole 51 and the sub-bearing body 75.

- Thus, the rotational force of the rotating shaft 70 is transmitted to the movable element 22. At this time, when the motor 16 starts rotating, the rod 106 of the reversal prevention mechanism 103 comes into sliding contact with the outer circumferential surface of the frame 14 at the initial stage, but when the number of rotations increases beyond a certain speed, the spring 107 is rotated by centrifugal force. Retracts against the force and maintains a completely non-contact state. Further, the cylindrical portion 35 of the movable element 22 is fitted with a small shaft 72 provided eccentrically with respect to the rotating shaft 70, and the Oldham mechanism 40
Since it is supported by the movable element 22, the movable element 22 performs a turning movement without rotation. Therefore, the scroll blades 34 provided on the movable element 22 also perform a swirling motion. Along with this swirling movement, the volume of the compression chamber P formed between the scroll blade 25 and the scroll [34] decreases periodically, and the compressed gas is thereby transferred to the discharge port 2.
It is discharged from 6. The discharged high pressure gas is stored in the cap 29.
It is sent out from the discharge pipe 113 through the gap 30 formed by the hole 31 provided in the cap 29 and the space 112. On the other hand 1. When the movable element 22 rotates as shown in F, cutout surfaces 36 and 27 are formed at the upper peripheral edge of the mirror plate 33 of the movable element 22 and at the inner edge of the annular wall 24 of the fixed element 21. It is effective that the peripheral edge of the compression chamber P is formed on the frame 14.
It is always in communication with the space above 5. The above-mentioned space communicates with the hole 58 through the holes 57 formed in the frame 14, and this hole 58 communicates with the opening 111a of the suction pipe 111 at a short distance.
The low-pressure gas is sucked into the low-pressure boat in the compression chamber P through the suction pipe 111, the hole 58, and the space on the surface 55, where the function of the compression device is exerted. In this case, even if a liquid such as a refrigerant is mixed into the low-pressure gas that has flowed in through the suction pipe 111, this liquid will fall downward while moving from the opening 111a to the hole 58. Therefore, the space 110 has exactly the same function as a gas-liquid separator.

On the other hand, when the motor 16 rotates as described above, the lubricating oil 1
A portion of 7 is pumped upward into the bore 90 by a centrifugal pump 1 with a configuration of 71.90. This pumped up flQill oil lubricates the inner circumferential surface of the bearing hole 51, then lubricates the fitting part between the small shaft 72 and the cylinder part 35, and then passes through the hole 117 to the Oldham mechanism 40. After that, a portion flows downward from the hole 58, and the remaining portion enters the compression chamber P to lubricate the sliding portion within the compression chamber P. The lubricating oil that has entered the compression chamber P is finally discharged from the discharge port 26 and then flows downward through the hole 32 and the hole 114 provided in the cap 29. Therefore, high pressure gas containing no lubricating oil is discharged from the discharge pipe 113.

Further, as described above, when the movable element 22 performs a rotational motion and a compression operation is performed, the pressure inside the compression chamber P becomes high, so the movable element 22 receives a downward thrust force of 1 J, and this force is 11114 n, frame 14 receiver 1
In addition to the surface 55, etc., there is a possibility that a burn-in phenomenon may occur in these elements. However, in this embodiment, the thrust 1-
The force-reducing grip 59 prevents the occurrence of burn-in phenomenon as follows.

That is, the annular body 60 of the thrust force reduction mechanism 59,
The annular space Q surrounded by the outer sealing ring 62, 63 and the mirror plate 33 always communicates with the so-called intermediate pressure ports s, s' of the compression chamber P via the holes 65, 66. Therefore, the end plate 33 receives an upward force due to the gas pressure in the annular space Q, and the presence of this force reduces the downward thrust force applied to the end plate 3'3. This reduction prevents the occurrence of the burn-in phenomenon. In addition,
The downward thrust force applied to the movable element 22 pulsates as the position of the compression space changes. For this reason, there is a risk that high-pressure gas may leak from the thrust force reduction mechanism 59 to the low-pressure side. However, in this embodiment, as shown in FIG. Since a leaf spring 64 is interposed between the inner and outer seal rings 62 and 63, the restoring force of the leaf spring 64 always presses the inner and outer seal rings 62, 63 against the lower surface of the mirror plate 33. Therefore, this fastening prevents leakage of high pressure gas.

Furthermore, when the motor 16 is stopped, there is a risk that the movable element 22 will rotate in the opposite direction due to the pressure difference between the space 112 and the space 110, causing high pressure gas to flow into the low pressure side. However, in the case of this embodiment, since a ratchet-type reversal prevention mechanism 103 is provided, the rod 106 of this mechanism 103 engages with the pawl 108 at the same time as the mechanism 103 stops, thereby reliably preventing the occurrence of reverse rotation. This prevents high-pressure gas from escaping.

In this way, the opening 111a of the suction pipe 111 located inside the sealed case 11 is placed close to the suction port of the scroll compression mechanism 15, that is, the hole 58 provided in the frame 14. Therefore, even if the motor 16 generates heat during operation, the amount of heat that the low-pressure gas receives from the motor 16 while moving to the hole 58 via the suction pipe 111 is extremely small. In other words, by arranging the opening 111a close to the hole 58, the thermal resistance between the motor 16 and the low-pressure gas flow path can be made sufficiently large. Therefore, the scroll-type compression mechanism 15 can always draw in low-temperature, low-pressure gas that is not affected by the heat generated by the motor 16, so that the above-mentioned effects can be obtained after all.

Note that the present invention is not limited to the embodiments described above. That is, in the embodiment, by bringing the opening 111a of the suction pipe 111 close to the hole 58, the motor 1
Although the thermal resistance between the motor 16 and the low pressure gas flow path is increased, a heat shield plate 200 may be provided above the motor 16 as shown in FIG. In addition, in the same figure, 201 is lll! 1 shows holes provided in the heat shield plate 200 to allow lubricating oil to flow downward. Further, the present invention can be applied to a so-called horizontal type, such as a shinoya in which the motor is disposed above the movable element.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of a scroll type compression device according to an embodiment of the present invention, FIG. 2(a) is a bottom view of a fixing element in the same device, and FIG. Figure 3 (
a) is a top view of a movable element in the same device, FIG. 4(b) is a sectional view taken along the line B-B in FIG. A perspective view, Fig. 5 is a plan view of the main parts of the Oldham mechanism in the device, Fig. 6 is a diagram for explaining the shape of the keyway of the Oldham mechanism, and Fig. 7 is a thrust force reduction built in the device. FIG. 8 is a longitudinal cross-sectional view of the mechanism, FIG. 8 is a cross-sectional view taken along line D--D in FIG. 1, and FIG. 9 is a longitudinal cross-sectional view of a scroll type compression device according to another embodiment of the present invention. 11... Sealed case, 14... Frame, 15...
・Scroll type compression mechanism, 16...Motor, 17...
・fl! I oil, 21... Fixed element, 22... Movable element, 25, 34... Scroll blade, 26... Discharge port, 40... Oldham mechanism, 51... Bearing hole, 59
... Thrust force reduction mechanism, 60... Annular body, 61.
...Annular groove, 62...Inner seal ring, 63...
Outer seal ring, 64...plate spring, 65.66...
- Hole as a communication path, 70...Rotating shaft, 73...Sub bearing, 74...Bearing support material, 75...Sub bearing body,
90... Hole for centrifugal pump, 100... Rotor, 1
01... Stator, 103... Reversal prevention mechanism, 110
, 112... Space, 111... Suction pipe, 111a.
...Opening, 113...Discharge pipe, 200...Heat shielding plate, P...Compression chamber, Q...Annular space. Applicant's representative Patent attorney Takehiko Suzue Figure 2 (a) (b) Figure 3 (a) (b) View 4 Figure 5 Figure 3a Figure 6

Claims (3)

[Claims] (1) A scroll consisting of a fixed element and a movable element, each of which is joined in the axial direction to form a compression chamber between them, and each of which has scroll blades that engage with each other within the compression chamber. A mold compression mechanism is disposed in a sealed case, and the movable element is caused to rotate by the power of a motor installed in the low-pressure atmosphere in the sealed case under the condition that the outer surface of the movable element is in a low-pressure atmosphere. In a scroll-type compression device that performs gas compression by rotating the scroll-type compression mechanism, the thermal resistance between the flow path of the low-pressure gas sucked into the scroll-type compression mechanism and the motor is increased in the closed case. A scroll type compression device characterized in that it is provided with means for causing. (2) The means for increasing the thermal resistance includes arranging an open end of a suction pipe, which guides low-pressure gas from the outside into the sealed case, located inside the sealed case, close to the suction port of the scroll-type compression mechanism. A scroll-type compression device according to claim 1, characterized in that the scroll-type compression device is constructed as follows. (3) The means for increasing the thermal resistance is a heat shielding plate provided in the sealed case so as to partition the flow path of the low-pressure gas from the space in which the motor is installed. A scroll type compression device according to claim 1.