JPH0921391A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To block the reverse flow so as to raise the oil pressure of an oil feeding pump, and to suppress the reverse rotation of the oil feeding pump by the oil pressure, by providing a check valve to block the flowing of the oil in the reverse direction to the suction direction, at the suction part of a displacement type oil feeding pump. SOLUTION: At the lower side of a cover plate 75, a suction pipe 88 to connect to a suction hole 82 is provided, and a check valve 89 is provided in the suction pipe 88. The suction pipe 88 sucks the lubricating oil OIL stored at the inner bottom part of an enclosed housing 31. The check valve 89 blocks the flow of the oil reverse to the oil flow when an oil pump P is operated in the rotation of the regular direction. That is, the flowing of the lubricating oil OIL inside a cylinder chamber 72 discharged to the inside of the housing 31 passing through the suction pipe 88, operated by the reverse rotation of a driving shaft 35 is blocked. Consequently, the oil pressure in the oil feeding pump P is raised, and the reverse rotation of the oil feeding pump P is suppressed by the raised oil pressure, so as to suppress the reverse rotation of the driving shaft 35.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type compressor provided with a positive displacement oil supply pump.

[0002]

2. Description of the Related Art In a scroll type compressor, as shown in FIG. 11, a compression mechanism C and an electric motor M are separately arranged inside a closed housing 1, and a drive shaft of the electric motor is connected to the compression mechanism. The drive shaft is rotated by the electric motor, and the compression mechanism is driven by the drive shaft. This scroll type compressor has been widely used as a compressor for a refrigerator and an air conditioner because it has a capability of operating with high efficiency.

The compression mechanism in the scroll compressor is
A pair of spiral blades, a fixed scroll and an orbiting scroll, are combined with each other to form a sealed space portion (movable fluid pocket) between them, and the orbiting scroll is turned by an electric motor to change the volume of the space portion. The gas is sucked from the suction port located on the outer peripheral side and discharged from the discharge port located at the center.

Generally, in a scroll compressor, the lubricating oil which is built in the lower end of the drive shaft and which is stored in the inner bottom of the hermetic housing is sucked into the sliding part of the compression mechanism through an oil supply hole formed inside the drive shaft. Oil pump for refueling (Fig. 11
Represented by medium P. ).

Conventionally, the oil pump provided in this hermetic compressor has the structure shown in FIGS. 12 and 13. In the figure, 1 is a closed housing. Reference numeral 2 denotes a bearing arranged at the inner bottom of the closed housing 1, which has a cylinder chamber 3 whose lower surface is open. The bearing 2 is fixed to the closed housing 1 by a stay 4 formed integrally therewith. The lower surface opening portion of the cylinder chamber 3 is closed by a thrust plate 5 and a cover plate 6 attached to the bearing 2.

Reference numeral 7 is a drive shaft, the lower end of which is inserted into the bearing 2, and an eccentric shaft 8 is formed at the lower end located in the cylinder chamber 3. Reference numeral 9 denotes an annular rotor arranged inside the cylinder chamber 3, which is rotatably fitted to the outer peripheral portion of the eccentric shaft 8 so that the outer peripheral surface contacts the inner peripheral surface of the cylinder chamber 3 and the It is limited to crescent.

A blade-shaped projection 10 extending in the diametrical direction is integrally formed on the outer peripheral portion of the rotor 9, and the slot 1 is formed on the inner peripheral surface of the cylinder chamber 3 along the small diameter direction.
1 is slidably inserted. The projection 10 partitions the cylinder chamber 3 into an oil supply chamber 3a and an oil discharge chamber 3b, and
Rotation of the rotor 9 is prevented. The outer periphery of the rotor 9 is circular except for the protrusion 10.

A suction hole 12 is formed in the cover plate 6 below the oil supply chamber 3a of the cylinder chamber 3 and communicates with the inner bottom of the closed housing 1.
The thrust plate 5 has a suction hole 12 and a suction port 13 communicating with the oil supply chamber 3 a of the cylinder chamber 3.

An oil supply groove 14 is formed in the cover plate 6, and the thrust plate 5 has a discharge port 15 communicating with the oil supply groove 14 and the oil discharge chamber 3b of the cylinder chamber 3, and the oil supply groove 14 and the drive shaft 4. Communication hole 1 communicating with oil supply hole 17
6 are formed respectively.

The oil supply hole 17 is formed in the drive shaft 4 along the axial direction from the lower end to the upper end. Lubricating oil OIL is stored in the inner bottom portion of the closed housing 1.
In this oil pump, since the protrusion 10 is integrally formed on the rotor 9, there is an advantage that the rotor can be prevented from being damaged and the number of parts is small.

When the oil pump thus constructed is rotated together with the drive shaft 7 rotated by the electric motor, the eccentric shaft 8 is eccentrically rotated in the direction of the arrow shown in the figure. The rotor 9 is pushed by the eccentric shaft 8 which is eccentrically rotated, and revolves revolvingly while the outer peripheral surface slides in line with the inner peripheral surface of the cylinder chamber 3 of the bearing 2. As the rotor 9 rotates, the respective volumes of the oil supply chamber 3a and the oil discharge chamber 3b in the cylinder chamber 3 increase and decrease relatively and change.

As the volume of the oil supply chamber 3a increases, the lubricating oil OIL stored in the inner bottom portion of the closed housing 1 passes through the suction hole 12 of the cover plate 6 and the suction port 13 of the thrust plate 5. Are sequentially sucked into the oil supply chamber 3a of the cylinder chamber 3. In addition, as the volume of the oil drainage chamber 3b of the cylinder chamber 3 decreases, the oil drainage chamber 3b
The lubricating oil OIL in the is pressurized and discharged from the discharge port 15 of the thrust plate 5.

The discharged lubricating oil OIL is supplied to the oil supply groove 14 of the cover plate 6 and the communication hole 16 of the thrust plate 5.
Through the lower end of the drive shaft 7 into the oil supply hole 17, flows out from the upper end of the drive shaft 7 through the oil supply hole 17 and is supplied to each sliding portion of the compression mechanism for lubrication. After that, the lubricating oil OIL flows down inside the closed housing 1 and accumulates at the bottom again.

[0014]

SUMMARY OF THE INVENTION A compression mechanism in a scroll compressor is a sequential space for sealing and compressing and transporting a fluid between side surfaces of a pair of spiral blades (a fixed scroll and an orbiting scroll) facing each other. Since it forms a part, it generally does not require a suction valve or a discharge valve.

However, when the operation of the compressor is unintentionally interrupted intentionally or due to the supply of electric power in accordance with the command, the compressed gas from the pressurized chamber and from the discharge chamber is discharged due to the closed space. Due to the reverse flow, there is a high possibility that reverse orbit of the orbiting scroll and reverse rotation of the drive shaft may occur.
Such reverse rotation often causes unpleasant noise in the compression mechanism of the scroll compressor, and when a single-layer electric motor is used as the electric motor in the scroll compressor, instantaneous power supply When the interruption occurs, the compression mechanism may start rotating in the opposite direction. When this reversal causes the compressor to be heated or damaged, and when the fan in the condenser used in the refrigerator or the like stops driving, the discharge pressure stalls the electric motor, or reverses or reverses the electric motor. It may increase up to the point of turning. In this case, the discharge pressure decreases as the orbiting scroll rotates in the reverse direction, and the electric motor again overcomes the pressure head to make the orbiting scroll "normal".
It is possible to obtain a state of being driven to rotate in the rotation direction. However, the discharge pressure rises to a pressure at which the forward and reverse rotation cycle is repeated again. Depending on such a forward / reverse cycle,
Damage to the compressor or related equipment.

Therefore, it has been demanded for the scroll type compressor in the related art to prevent the reverse rotation of the compression mechanism and prevent various problems due to the reverse rotation. The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a scroll compressor that prevents reverse rotation of a compression mechanism and prevents various problems due to this reverse rotation.

[0017]

According to another aspect of the present invention, there is provided a scroll type compressor in which a motor and a scroll compression mechanism connected to each other via a drive shaft are housed in a housing, and the drive shaft is connected to one end of the drive shaft. In a scroll compressor provided with a positive displacement oil supply pump incorporating a shaft, a check valve for preventing oil from flowing in a direction opposite to a suction direction is provided at a suction portion of the positive displacement oil supply pump. It is characterized by

According to this structure, when the drive shaft rotates in the reverse direction, the check valve blocks the reverse flow in the oil supply pump, so that the oil pressure in the oil supply pump increases, and the increased oil pressure causes the oil supply pump to reverse. As a result, the reverse rotation of the drive shaft is suppressed. As a result, reverse rotation of the scroll compression mechanism is suppressed.

According to the scroll type compressor of the invention of claim 2,
2. The scroll compressor according to claim 1, wherein the oil in the housing when the drive shaft rotates in the reverse direction is discharged from the discharge section of the positive displacement oil pump to the discharge section of the positive displacement oil pump. The mold refueling pump is characterized by being provided with a check valve for permitting suction.

According to this structure, in addition to the effect of stopping the drive shaft according to the first aspect of the present invention, since oil is sucked into the oil supply pump from the suction portion, the oil pressure inside the oil supply pump further rises. As a result, the increased hydraulic pressure further suppresses the reverse rotation of the oil supply pump.

According to the scroll type compressor of the invention of claim 3,
The scroll compressor according to claim 1, wherein when the drive shaft rotates in a reverse direction, an oil passage for introducing oil whose pressure has increased from a suction portion of the positive displacement oil supply pump and a pressure of the oil introduced from the oil passage are provided. And a braking body that receives and applies a braking force to the drive shaft.

According to this structure, in addition to the effect of stopping the drive shaft according to the invention of claim 1, the brake body is operated by the raised hydraulic pressure inside the oil supply pump to brake the drive shaft. Therefore, the oil supply pump is hydraulically operated. The reversal of is suppressed more strongly.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the invention of claim 1 of the present application will be described with reference to FIGS. First,
A scroll type compressor as an example of a hermetic type compressor provided with the oil pump of the present invention will be described with reference to FIG.

In FIG. 1, the interior of the closed housing 31 is partitioned by a discharge cover 32 into a high pressure space 33 and a low pressure space 34. Inside the low-pressure space 34, a scroll-type compression mechanism C is provided in an upper part, and an electric motor M is provided in a lower part.
However, the oil pumps P of the present invention are further provided at the bottom of the low-pressure space 34 (bottom of the closed housing 31), and these are the scroll type compression mechanism C, the electric motor M, and the oil pump P.
Are connected by a drive shaft 35 provided in the electric motor M.

The electric motor M has a stator 36 fixed to the hermetic housing 31, a rotor 37 assembled inside the stator 36, and a drive shaft 3 inserted and fixed to the rotor 37.
5, the drive shaft 35 extends below and above the rotor 37, respectively.

The scroll type compression mechanism C has a fixed scroll 38 and an orbiting scroll 39, and the fixed scroll 3
8 includes an end plate 40 and a spiral wrap 41,
The discharge port 42 is provided in the. The orbiting scroll 39 includes an end plate 43 and a spiral wrap 44, and
A bush 46 is rotatably fitted into a boss 45 provided on the lower surface of the bush 3 via a bearing 47.
An eccentric shaft 48 provided at the upper end of the drive shaft 35 is slidably inserted into the drive shaft 6.

Fixed scroll 38 and orbiting scroll 39
The end plate 40 and the end plate 43 are eccentric by a predetermined distance, and a plurality of closed spaces 49 are formed in which the wrap 41 and the wrap 44 are mutually combined at an angle of 180 degrees. The orbiting scroll 39 is slidably supported by a casing 50 fixed inside the closed housing 31, and between the orbiting scroll 39 and the casing 50,
A rotation preventing mechanism 51 is provided which allows the orbiting scroll 39 to orbit but does not rotate.

The outer periphery of the end plate 40 of the fixed scroll 38 is supported by a casing 50 so as to be floatable, and cylindrical flanges 52, 53 are provided on the upper surface of the end plate 40 of the fixed scroll 38.
Are arranged concentrically.

A back pressure chamber 55 is formed between the cylindrical flanges 52 and 53 by fitting a cylindrical flange 54 provided on the lower surface of the discharge cover 32 in a sealed and slidable manner. The back pressure chamber 55 communicates with a closed space 49 in the middle of gas compression through a hole 56 provided in the end plate 40. Here, the hole 56 is located at a point in contact with the inner peripheral side of the wrap 41, and the high pressure chamber 57 is located on the inner peripheral side of the back pressure chamber 55.
Is formed, and a low pressure chamber 58 is formed on the outer peripheral side.
A gas suction pipe 59 is provided in the low pressure space 34 of the closed housing 31, and a gas discharge pipe 60 is provided in the high pressure space 35.

In such a structure, the drive shaft 35 is rotated by driving the motor M, and this rotation is transmitted to the orbiting scroll 39 of the compression mechanism C via the eccentric shaft 48, the bush 46 and the boss 45. The orbiting scroll 39 makes a revolution revolving motion on a circular orbit having a radius of the revolution revolution radius while being prevented from rotating by the rotation inhibiting mechanism 51.

Then, the gas enters the low-pressure space 34 of the closed housing 31 through the suction pipe 59, and is sucked into the closed section of the compression mechanism C via a path not shown. And
The closed space 4 is formed by the orbiting motion of the orbiting scroll 39.
As the volume of the gas 9 decreases, the gas is compressed and reaches the central portion, enters the high pressure space 33 from the discharge port 42 through the high pressure chamber 57, and is discharged to the outside through the gas discharge pipe 60.

At this time, the fixed scroll 38 is pressed against the orbiting scroll 39 by the gas pressure in the high pressure chamber 57 and the back pressure chamber 55 to prevent the gas from leaking from the inside of the closed space 49. When the liquid is sucked into the closed space 49, the fixed scroll 38 floats up and allows the liquid to escape, thereby preventing damage to the compression mechanism.

Next, one embodiment of the invention of the oil pump P which is the object of the present invention will be described with reference to FIGS. 1 to 5. Reference numeral 71 in the drawing denotes a cylinder arranged and fixed to the inner bottom portion of the closed housing 31, and this has a cylinder chamber 72 whose lower surface portion is open. The bearing 71 is fixed to the closed housing 31 by a stay 73 formed integrally therewith. The lower surface opening of the cylinder chamber 72 is a bolt 90.
Is closed by a thrust plate 74 and a cover plate 75, which are examples of a closing member attached to the bearing 71.

The lower end of the drive shaft 35 is inserted into the bearing 71, and the eccentric shaft 76 is formed at the lower end located in the cylinder chamber 72. Reference numeral 77 denotes an annular rotor arranged inside the cylinder chamber 72. The rotor 77 is rotatably fitted to the outer peripheral portion of the eccentric shaft 76, the outer peripheral surface of which contacts the inner peripheral surface of the cylinder chamber 72, so that the cylinder chamber 72 is closed. It is limited to crescent.

A blade-shaped protrusion 78 extending in the diametrical direction is integrally formed on the outer peripheral portion of the rotor 77, and is slidable in a slot 79 formed in the inner peripheral surface of the cylinder chamber 72 along the diametrical direction. Has been inserted into. This protrusion 78
Divides the cylinder chamber 72 into an oil supply chamber 80 and an oil discharge chamber 81, and prevents rotation of the rotor 77.

A suction hole 82 is formed in the cover plate 75 below the oil supply chamber 80 of the cylinder chamber 72, and the suction hole 82 communicates with the inner bottom portion of the closed housing 31. The thrust plate 74 has a suction hole 82 and a suction port 83 communicating with the oil supply chamber 80 of the cylinder chamber 72.

The cover plate 75 has a discharge hole 84.
And a discharge port 85 communicating with the discharge hole 84 and the oil discharge chamber 81 of the cylinder chamber 72 is formed in the thrust plate 74.
And a communication hole 86 that communicates with the discharge hole 84 and the oil supply hole 87 of the drive shaft 35, respectively. The oil supply hole 87 is formed in the drive shaft 35 from the lower end to the upper end along the axial direction.

A suction hole 8 is provided below the cover plate 75.
2 is provided with a suction pipe 88, and this oil supply pipe 88
A check valve 89 is provided inside. Suction pipe 88
Is for sucking the lubricating oil OIL stored in the inner bottom portion of the closed housing 31. The check valve 89 is an oil pump P.
Is to prevent the flow of oil opposite to the flow of oil when operating in the forward rotation. That is, the oil pump P, in other words, the drive shaft 35 operates in the forward rotation to allow the lubricating oil OIL of the housing 31 to be sucked into the cylinder chamber 72 through the suction pipe 88, and the oil pump P,
In other words, the drive shaft 35 operates in the reverse direction to prevent the lubricating oil OIL inside the cylinder chamber 72 from passing through the suction pipe 88 and being discharged into the housing 31.

Reference numeral 91 is a nut for closing the lower opening 84a of the discharge hole 84. The oil pump configured in this way
With the drive shaft 35 rotated by the electric motor M, the eccentric shaft 35 is eccentrically rotated in the arrow direction shown in FIG. Rotor 7
7 is pushed by an eccentric shaft 76 that rotates eccentrically, and makes an orbital revolving motion while the outer peripheral surface slides in line with the inner peripheral surface of the cylinder chamber 72 of the bearing 71. Cylinder chamber 7 accompanying rotation of rotor 77
The respective capacities of the oil supply chamber 80 and the oil discharge chamber 81 in 2 change relative to each other.

As the volume of the oil supply chamber 80 increases, the lubricating oil OIL stored in the inner bottom portion of the closed housing 31 is sucked through the suction pipe 88 and the check valve 89, and the cover plate It is sequentially sucked into the oil supply chamber 80 of the cylinder chamber 72 through the suction hole 82 of 75 and the discharge port 85 of the thrust plate 74. Further, as the volume of the oil discharge chamber 81 in the cylinder chamber 72 decreases, the lubricating oil OIL in the oil discharge chamber 81 is pressurized and discharged from the discharge port 85 of the thrust plate 74.

The discharged lubricating oil OIL is sent from the lower end of the drive shaft 35 to the oil supply hole 87 through the discharge hole 84 of the cover plate 75 and the communication hole 86 of the thrust plate 74. The flow of oil so far is shown by the arrow in FIG. After that, it flows out from the upper end of the drive shaft 35 through the oil supply hole 87 and is supplied to each sliding portion in the compression mechanism C to perform lubrication. After that, the lubricating oil OIL is sealed in the closed housing 31.
It flows down the inside of and accumulates at the bottom again.

By the way, when the compression mechanism C is rotated in the reverse direction after the operation of the compression mechanism C is stopped, the drive shaft 35 is rotated in the reverse direction and the rotor 77 of the oil pump P is moved as shown by the broken line arrow in FIG. Reverse rotation. In this case, the suction and discharge of the lubricating oil OIL in the oil pump P are opposite to those in the normal rotation, and the flow of the lubricating oil OIL inside the oil pump P is also opposite to that in the normal rotation shown in FIG. Become.

Here, a check valve 89 is provided in the suction pipe 88, which is the suction portion of the oil pump P, for blocking the flow of oil during normal rotation, that is, the flow in the discharge direction opposite to the flow in the oil suction direction. Is provided. Therefore, the check valve 89 blocks the flow in the suction pipe 88 in the discharge direction. As a result, the flow path of the lubricating oil OIL up to the check valve 89 during reverse rotation, especially the hydraulic pressure inside the suction pipe 88 and the oil pump P, increases. The reverse rotation of the rotor 77 of the oil pump P is suppressed by the torque due to the increase in the hydraulic pressure, and as a result, the reverse rotation of the drive shaft 35 is suppressed and the compression mechanism C
The reverse rotation of is suppressed.

Therefore, it is possible to prevent various troubles such as the generation of unpleasant noise accompanying the reverse rotation of the compression mechanism C and the damage of the compression mechanism C. In addition, it is a suction valve or discharge valve mechanism that restricts or rotates the reverse flow of compressed gas that causes a problem of reverse rotation by using a one-way clutch, which is expensive and positively improves the efficiency of the compression mechanism. It is not necessary to provide a valve mechanism for lowering.

In this embodiment, the check valve 89 is provided at a position near the suction port of the suction pipe 88. However, the check valve is not limited to this, and the check valve is in the oil flow direction with respect to the suction port of the oil pump P. It should be provided on the upstream side. For example, a check valve may be provided inside the cover plate. Further, the check valve is not limited to be provided laterally.

Next, an embodiment of the invention of claim 2 will be described with reference to FIG. 6, the same parts as those in FIG. 5 are designated by the same reference numerals. In addition to the configuration and effect of the embodiment of the invention of claim 1 described above, the embodiment of the present invention is a second connecting part of the discharge hole 84 below the cover plate 75 of the oil pump P. The second suction pipe 101 is provided with a check valve 102 (the oil flow direction is also the same as the check valve 89) for preventing the reverse flow of the oil at the time of normal rotation, thereby providing a reverse rotation prevention effect. It is getting higher.

That is, when the oil pump P operates in the normal rotation, the check valve 102 operates because the pressure of the discharge portion of the oil pump P is high, and the lubricating oil inside the oil pump P discharges the cover plate 75. The oil does not flow out from the hole 84 to the second suction pipe 101, and as a result, the oil supply operation of the oil pump P is performed without any trouble. When the oil pump P operates in the reverse rotation, the lubricating oil OIL in the inner bottom portion of the closed housing 31.
Is sucked into the oil pump P from the second suction pipe 101 via the check valve 102. Therefore, in addition to the hydraulic pressure increase in the oil pump P according to the embodiment of the invention of claim 1,
The oil pressure in the oil pump P is further increased, the force for reliably suppressing the reverse rotation operation of the oil pump P is further increased, and the reverse rotation prevention effect is further enhanced.

Next, an embodiment of the invention of claim 3 will be described with reference to FIGS. 7 to 10. 7 to 1
0, the same parts as those in FIGS. 1 to 5 are denoted by the same reference numerals.

In the embodiment shown in FIG. 7, the bearing 71 is formed with a circular recess 112 surrounding the drive shaft 35 and an oil passage 113 connecting the recess 112 to the cylinder chamber 72 of the bearing 71. An annular braking member 111 that surrounds and contacts the drive shaft 35 is provided.

According to this structure, as shown in the embodiment of the invention of claim 1, the lubricating oil OI having the increased pressure of the oil pump P generated by the action of the check valve.
L reaches the recess 112 through the oil passage 113 to reach the brake body 1.
Act on 11. Therefore, the braking body 111 is pressed around the drive shaft 35 that rotates in the reverse direction to apply the braking force. Therefore, in addition to the increase in the hydraulic pressure in the oil pump P according to the embodiment of the invention of claim 1, the oil pump The oil pressure in P further increases, the force for reliably suppressing the reverse rotation operation of the oil pump P further increases, and the reverse rotation prevention effect is further enhanced.

In the embodiment shown in FIG. 8, a pair of grooves 121 extending along the drive shaft 35 are formed at positions facing each other across the drive shaft 35 in the bearing 71, and the pair of grooves 121 are formed in the bearing 71. A pair of oil passages 122 connected to the cylinder chamber 72 are formed, and a braking body 123 is arranged in the pair of grooves 121 so as to be movable in a direction toward and away from the drive shaft 35.

According to this structure, as shown in the embodiment of the invention of claim 1, the lubricating oil OI having the increased pressure of the oil pump P generated by the action of the check valve.
L reaches the recess 121 from the discharge hole 84 of the oil pump P through the oil passage 122 and acts on the braking body 123. As a result, the pair of braking bodies 23 are pressed around the drive shaft 35 that rotates in the reverse direction to apply a braking force. Therefore, in addition to the increase in the hydraulic pressure in the oil pump P according to the embodiment of the invention of claim 1, The oil pressure in the pump P is further increased, the force for reliably suppressing the reverse rotation operation of the oil pump P is further increased, and the reverse rotation prevention effect is further enhanced.

In the embodiment shown in FIG. 9, a pair of grooves 121 extending along the drive shaft 35 are formed at positions facing each other across the drive shaft 35 in the bearing 71, and the pair of grooves 121 are formed in the bearing 71. A pair of oil passages 122 connected to the cylinder chamber 72 are formed, and a braking body 124 is arranged in the pair of grooves 121 so as to be movable in a direction toward and away from the drive shaft 35.

The braking member 123 has a thick portion 124 at both upper and lower ends.
b, the portion sandwiched between these thick portions 124b is the thin portion 12
4a. In the pair of grooves 121, the pair of oil passages 122 are opened in the space portion sandwiched by the thick portion 124b and the thin portion 124a.

According to this structure, as shown in the embodiment of the invention of claim 1, the lubricating oil OI having the increased pressure of the oil pump P generated by the action of the check valve.
L reaches the pair of grooves 121 from the discharge hole 84 of the oil pump P through the pair of oil passages 122 and acts on the pair of braking bodies 124. In this case, when the pressure inside the pair of grooves 121 rises, the thin-walled portions 124a of the pair of braking bodies 124 press the drive shaft 35 that rotates in the reverse direction to apply the braking force. The thick portions 124b of the pair of braking bodies 124 are engaged with the pair of grooves 121 to prevent the pair of braking bodies 124 from trying to rotate together with the drive shaft 35. When the drive shaft 35 is rotated in the reverse direction, the discharge port of the oil pump P is blocked and the pressure becomes higher than the discharge pressure at the time of forward rotation. Therefore, the deformation of the thin portion 124a of the pair of braking bodies 124 does not cause oiling. Braking force does not work with pressure,
It can be selectively operated so that the braking action is performed only during reverse rotation.

For this reason, the pair of braking bodies 124 are connected to the drive shaft 3
5, the braking force is applied to the periphery of the oil pump 5. Therefore, in addition to the increase in the oil pressure in the oil pump P according to the embodiment of the invention of claim 1, the oil pressure in the oil pump P is further increased, and the oil pump P is increased. The force that reliably suppresses the reverse rotation operation of P is further increased, and the reverse rotation prevention effect is further enhanced.

In the embodiment shown in FIG. 10, a recess 131 is formed in the upper end of the bearing 71, and an oil passage 132 is formed to connect the recess 131 to the cylinder chamber 72 of the oil pump P. The recess 131 is formed above the recess 131. Disc-shaped braking bodies 133, 134
Is arranged.

According to this structure, the oil whose pressure has risen in the cylinder chamber 72 of the oil pump P is passed through the oil passage 132 to the recess 1
Then, the braking bodies 133 and 134 are pressed to the lower end surface of the rotor 37 of the electric motor M to stop the rotor 37 and the drive shaft 35 that rotate in the reverse direction. This configuration can also obtain the same effects as those of the above-described embodiments. The present invention is not limited to the embodiments of the invention described above, and various modifications can be carried out.

[0059]

As described above, according to the scroll type compressor of the first aspect of the present invention, the electric motor and the scroll compression mechanism connected to each other through the drive shaft are housed inside the housing, and one end of the drive shaft is included. In a scroll compressor provided with a positive displacement oil supply pump incorporating a coaxial shaft, a check valve for preventing oil from flowing in a direction opposite to a suction direction is provided in a suction portion of the positive displacement oil supply pump. Therefore, when the drive shaft rotates in the reverse direction, the check valve blocks the reverse flow in the refueling pump, and the hydraulic pressure in the refueling pump rises. Reverse rotation of the axis is suppressed. As a result, reverse rotation of the scroll compression mechanism can be suppressed. Therefore, it is possible to prevent the reverse rotation of the compression mechanism in the scroll compressor and prevent various problems due to the reverse rotation.

According to the scroll type compressor of the invention of claim 2, in the scroll type compressor of claim 1,
Allow the discharge part of the positive displacement oil pump to suck the oil inside the housing when the drive shaft rotates in the reverse direction from the discharge part of the positive displacement oil pump into the positive displacement oil pump. In addition to the effect of stopping the drive shaft according to the invention of claim 1, since the oil is sucked from the suction portion into the oil supply pump, the oil pressure inside the oil supply pump is further increased. As the hydraulic pressure rises, the reverse rotation of the oil supply pump is further strongly suppressed by the increased hydraulic pressure.

According to the scroll compressor of the invention of claim 3, in the scroll compressor of claim 1,
An oil passage that guides the oil whose pressure has increased from the suction portion of the positive displacement oil pump when the drive shaft rotates in the reverse direction, and a braking body that receives the pressure of the oil introduced from the oil passage and applies a braking force to the drive shaft. Is provided, in addition to the effect of stopping the drive shaft according to the first aspect of the invention, the braking body is operated by the raised hydraulic pressure inside the oil supply pump to brake the drive shaft. Reversal can be suppressed more strongly.

[Brief description of drawings]

FIG. 1 is a sectional view showing a compressor which is an embodiment of the invention of claim 1.

FIG. 2 is a sectional view showing an oil pump in the compressor of the same embodiment.

FIG. 3 is a sectional view taken along the line AA in FIG. 2;

FIG. 4 is a perspective view showing an oil pump in the compressor of the same embodiment.

FIG. 5 is an exploded perspective view showing an oil pump in the compressor of the same embodiment.

FIG. 6 is an exploded perspective view showing an oil pump in the compressor according to the second embodiment of the invention.

FIG. 7 is a sectional view showing an oil pump in the compressor according to the first embodiment of the invention of claim 3;

FIG. 8 is a sectional view showing an oil pump in a compressor which is a second embodiment of the invention according to claim 3;

FIG. 9 is a sectional view showing an oil pump in a compressor which is a third embodiment of the invention of claim 3;

FIG. 10 is a sectional view showing an oil pump in a compressor which is a fourth embodiment of the invention according to claim 3;

FIG. 11 is a sectional view showing a conventional compressor.

FIG. 12 is a sectional view showing an oil pump in a conventional compressor.

13 is a sectional view taken along the line BB of FIG.

[Explanation of symbols]

 31 ... Housing, 35 ... Drive shaft, 36 ... Stator, 37 ... Rotor, 38 ... Fixed scroll, 39 ... Orbiting scroll, 71 ... Bearing, 72 ... Cylinder chamber, 74 ... Thrust plate, 75 ... Cover plate, 76 ... Eccentric shaft, 77 ... Rotor, 80 ... Oil supply chamber, 81 ... Oil discharge chamber, 82 ... Suction hole, 84 ... Discharge hole, 87 ... Oil supply hole, 89 ... Check valve, 101 ... Suction pipe, 102 ... Check valve, 111 ... Braking body, 121 ... Braking body, 124 ... Braking body, 133 ... Braking body, C ... Compression mechanism, M ... Electric motor, P ... Pump.

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[Procedure amendment]

[Submission date] May 27, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0015

[Correction method] Change

[Correction contents]

However, when the operation of the compressor is unintentionally interrupted intentionally or due to the supply of electric power in accordance with the command, the compressed gas from the pressurized chamber and from the discharge chamber is discharged due to the closed space. Due to the reverse flow, there is a high possibility that reverse orbit of the orbiting scroll and reverse rotation of the drive shaft may occur.
Such reverse rotation often causes unpleasant noise in the compression mechanism of the scroll compressor. Further, when a single- phase electric motor is used as the electric motor in the scroll compressor, the compression mechanism may start rotating in the reverse direction when the power supply is momentarily cut off. This reversal may cause compressor heating or damage, and when the fan in the condenser used in the refrigerator or the like stops driving, the discharge pressure stalls the motor or causes the motor to rotate in reverse . It may increase to some extent. In this case, the discharge pressure decreases as the orbiting scroll rotates in the reverse direction, and the electric motor again overcomes the pressure head to drive the orbiting scroll in the "forward" rotation direction. However, the discharge pressure rises to a pressure at which the forward and reverse rotation cycle is repeated again.
Such forward and reverse cycles cause damage to the compressor or associated equipment.

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0037

[Correction method] Change

[Correction contents]

The cover plate 75 has a discharge hole 84.
Is formed in the thrust plate 74, and a discharge port 85 communicating with the discharge hole 85 and the oil discharge chamber 81 of the cylinder chamber 72 is formed.
And a communication hole 86 that communicates with the discharge hole 84 and the oil supply hole 87 of the drive shaft 35, respectively. The oil supply hole 87 is formed in the drive shaft 35 from the lower end to the upper end along the axial direction.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0039

[Correction method] Change

[Correction contents]

Reference numeral 91 is a relief formed under the discharge hole 84.
This is a check valve that opens and closes the hole 84a. In the oil pump configured as described above, the eccentric shaft 35 is eccentrically rotated in the arrow direction shown in FIG. 3 together with the drive shaft 35 rotated by the electric motor M. The rotor 77 is pushed by the eccentric shaft 76 that eccentrically rotates, and makes an orbital revolving motion while the outer peripheral surface slides in line with the inner peripheral surface of the cylinder chamber 72 of the bearing 71. With the rotation of the rotor 77, the oil supply chamber 80 and the oil discharge chamber 8 in the cylinder chamber 72
The respective volumes of 1 are relatively increased or decreased and changed.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0040

[Correction method] Change

[Correction contents]

As the volume of the oil supply chamber 80 increases, the lubricating oil OIL stored in the inner bottom portion of the closed housing 31 is sucked through the suction pipe 88 and the check valve 89, and the cover plate It is sequentially sucked into the oil supply chamber 80 of the cylinder chamber 72 through the suction hole 82 of 75 and the suction port 83 of the thrust plate 74. Also,
As the volume of the oil discharge chamber 81 in the cylinder chamber 72 decreases, the lubricating oil OIL in the oil discharge chamber 81 is pressurized and discharged from the discharge port 85 of the thrust plate 74.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0044

[Correction method] Change

[Correction contents]

Therefore, it is possible to prevent various troubles such as the generation of unpleasant noise accompanying the reverse rotation of the compression mechanism C and the damage of the compression mechanism C. Also, it should reverse rotation problems backflow of compressed gas to cause a suction valve or discharge valve mechanism is limited or turned, provided proactively valve mechanism that reduces the efficiency of the compression mechanism together with the costly Disappears.

[Procedure correction 6]

[Document name to be amended] Statement

[Correction target item name] 0046

[Correction method] Change

[Correction contents]

Next, an embodiment of the invention of claim 2 will be described with reference to FIG. 6, the same parts as those in FIG. 5 are designated by the same reference numerals. Embodiments of the invention, in addition to the configuration <br/>及beauty effects in the embodiment of the invention of claim 1 described above, a portion of the discharge hole 84 on the lower side of the cover plate 75 of the oil pump P Is provided with a second suction pipe 101, and the second suction pipe 101 is provided with a check valve 102 (the oil flow direction is also the same as the check valve 89) for preventing a reverse flow of oil during normal rotation, The reverse rotation prevention effect is further enhanced.

[Procedure amendment 7]

[Document name to be amended] Statement

[Correction target item name] 0055

[Correction method] Change

[Correction contents]

According to this structure, as shown in the embodiment of the invention of claim 1, the lubricating oil OI having the increased pressure of the oil pump P generated by the action of the check valve.
L reaches the pair of grooves 121 from the discharge hole 84 of the oil pump P through the pair of oil passages 122 and acts on the pair of braking bodies 124. In this case, when the pressure inside the pair of grooves 121 rises, the thin-walled portions 124a of the pair of braking bodies 124 press the drive shaft 35 that rotates in the reverse direction to apply the braking force. The thick portions 124b of the pair of braking bodies 124 are engaged with the pair of grooves 121 to prevent the pair of braking bodies 124 from trying to rotate together with the drive shaft 35. Because when driving shaft 35 reverses We discharge port of the oil pump P is blocked by Beth, because a higher pressure than the discharge pressure during forward rotation, deformation of the thin portion 124a of the pair of brake members 124 The braking force does not work at the refueling pressure,
It can be selectively operated so that the braking action is performed only during reverse rotation.

[Procedure amendment 8]

[Document name to be amended] Drawing

[Correction target item name] Fig. 1

[Correction method] Change

[Correction contents]

FIG.

[Procedure amendment 9]

[Document name to be amended] Drawing

[Correction target item name] Figure 3

[Correction method] Change

[Correction contents]

[Figure 3]

[Procedure amendment 10]

[Document name to be amended] Drawing

[Name of item to be corrected] Figure 7

[Correction method] Change

[Correction contents]

FIG. 7

[Procedure amendment 11]

[Document name to be amended] Drawing

[Name of item to be corrected] Fig. 10

[Correction method] Change

[Correction contents]

FIG. 10

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kounen Takeda 3-1, Asahi-cho, Nishibiwajima-cho, Nishikasugai-gun, Aichi Prefecture Mitsubishi Heavy Industries, Ltd. Air Conditioning Factory

Claims (3)

[Claims] 1. A scroll-type compression system in which a motor and a scroll compression mechanism connected to each other via a drive shaft are housed in a housing, and a positive displacement oil pump incorporating the drive shaft is provided at one end of the drive shaft. In the machine, a scroll valve is provided in a suction portion of the positive displacement oil supply pump, which is provided with a check valve for preventing oil from flowing in a direction opposite to a suction direction. 2. The oil in the housing when the drive shaft rotates in the reverse direction is sucked into the discharge portion of the positive displacement oil pump from the discharge portion of the positive displacement oil pump to the inside of the positive displacement oil pump. The scroll compressor according to claim 1, further comprising a check valve that allows the compressor to be shut down. 3. An oil passage for guiding oil whose pressure has increased from the suction portion of the positive displacement oil pump when the drive shaft rotates in the reverse direction, and a control for the drive shaft by receiving the pressure of the oil introduced from the oil passage. The scroll-type compressor according to claim 1, further comprising a braking body that applies power.