JP3274900B2 - Refueling pump device in compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is provided on a rotating shaft of a compressor for supplying oil to a compression mechanism.
In particular, the present invention relates to an improvement in a positive displacement type refueling pump device.

[0002]

2. Description of the Related Art Regardless of the type and structure of a compression mechanism, such as a rotary compressor or a scroll compressor, an oiling means is provided to ensure the compression mechanism and ensure smooth slidability. .

[0003] The oiling means of such a compressor also has various structures, but it is necessary to ensure a sufficient amount of oiling and to satisfy the requirement of preventing accidental burning damage.
A positive displacement refueling pump device is optimal. So-called trochoid pumps and gear pumps are representative of positive displacement pumps, and it is conceivable to apply them as refueling pumps. However, these pumps have a complicated structure, a large number of parts, are poor in workability and assemblability, are costly, and are not common. FIGS. 5 (A) and 5 (B) show a displacement type refueling pump device which has been developed to solve these problems as much as possible and which is frequently used.

[0004] In the figure, reference numeral 1 denotes a rotary shaft, and an oil supply pump device provided at the lower end is immersed in a lubricating oil surface of an oil reservoir. An oil supply hole 2 is provided from the lower end surface of the rotating shaft 1 along the axis. The oil supply hole 2 extends to a compression mechanism (not shown).

[0005] Further, a concave groove 3 is provided in the distal end surface of the rotating shaft 1 in the radial direction, and the rotation preventing portion 5 of the connecting pin 4 is engaged. The connection pin 4 has a hollow pipe shape, and an upper portion from the rotation preventing portion 5 is fitted into the oil supply hole 2.

The lower portion from the rotation preventing portion 5 is rotatably engaged with the thrust plate 6 and is fitted to and integrated with the pump shaft 7. Further, the lower end surface of the connection pin 4 is supported on the seal plate 8 and the fixed plate 9.

[0007] The outer peripheral surface of the pump shaft 7 is eccentric with respect to the connecting pin and the rotary shaft 1, and the pump cylinder 10
Are accommodated in a cylinder chamber 11 formed in the cylinder. In a state where the inside of the cylinder chamber 11 is eccentrically rotated, a part of the peripheral surface thereof is always in rolling contact with a part of the peripheral surface of the cylinder chamber 11.

The fixed plate 9, the seal plate 8, the pump cylinder 10 and the thrust plate 6 are sequentially stacked, and are fixed via fixing bolts 12 to an auxiliary bearing which also serves as the pump device main body 13.

A cutout groove 14 is formed in a part of the peripheral surface of the pump shaft 7.
Are provided, and the slide pin 15 is movably engaged. When the pump shaft 7 rotates via the connecting pin 4 together with the rotating shaft 1, the slide pin 15
Moves to the peripheral end side of the notch groove 14 and slides on the peripheral surface of the cylinder chamber 11. At the same time, the slide pin 15 divides the cylinder chamber into two except when the cylinder chamber 11 rolling contact portion of the pump shaft 7 coincides with the slide pin 15 position.

[0010] Oil suction holes 16, 16 penetrating through the plate thickness of each other are provided between the fixed plate 9 and the seal plate 8, and are formed in oil suction grooves 17 provided facing the cylinder chamber 11 of the pump cylinder 10. Communicate.

At another position facing the cylinder chamber 11 of the pump cylinder 10, an oil discharge notch 18 is provided, and an oil discharge hole 19 provided in the seal plate 8 and an oil guide groove 20 provided in the fixed plate 9 are formed. Connect to one end.

The oil guide groove 20 is provided only on the overlapping surface with the seal plate 8, and the other end of the oil guide groove 20 extends so as to communicate with at least the hollow portion of the connecting pin 4. Is established.

With the oil supply pump device having such a structure, the pump shaft 7 makes an eccentric rotation in the cylinder chamber 11 with the rotation of the rotary shaft 1, and the slide pin 15 makes the cylinder while the cylinder chamber 11 is divided into two. It slides on the peripheral wall of the chamber 11.

A negative pressure is generated in accordance with the change in the capacity of the divided cylinder chambers 11, and the lubricating oil in the oil reservoir is sucked from the oil suction hole 16 and guided into the cylinder chamber 11. The lubricating oil collects in the cylinder chamber 11 that is divided on the rotation direction side, and receives pressure due to a decrease in the capacity of the cylinder chamber 11 due to the movement of the slide pin 15.

The lubricating oil, which has risen to a predetermined pressure, is discharged from the oil discharge notch 18 to form an oil discharge hole 19 and an oil guide groove 20.
Through the connection pin 4 and through the oil supply hole 2
To the compression mechanism.

[0016]

As described above, it cannot be denied that reliable lubrication is achieved, but it still has a large number of parts, poor assemblability, and a cost problem.

Further, as a feature of the positive displacement pump including the trochoid pump described above, oil is supplied in proportion to the rotation speed of the rotating shaft 1, so that when the rotation speed becomes high, Unnecessary and excessive refueling,
As the time elapses, the amount of oil discharged to the outside of the compressor increases, and the oil level in the oil sump decreases. That is, a problem remains in terms of reliability.

The present invention has been made in view of the above circumstances, and a first object is to simplify the structure with a smaller number of parts, improve workability and assemblability, and Provided is a refueling pump device in a compressor that can reliably perform refueling and obtain improved refueling efficiency.

A second object is to improve the reliability by suppressing the amount of lubrication at the time of high-speed rotation of the rotating shaft, thereby extremely reducing the oil level in the oil reservoir and reducing the amount of oil discharge. An oil supply pump device in a compressor is provided.

[0020]

According to the present invention, there is provided a refueling pump device for a compressor according to the first aspect of the present invention.

A pump cylinder provided at an end of the rotating shaft and having a cylinder chamber formed eccentrically with respect to the axis of the rotating shaft so that a part of the peripheral surface of the rotating rotating shaft is always in rolling contact with a fixed portion. A seal plate provided on one end face of the pump cylinder and closing one end open face of the cylinder chamber;
A thrust plate provided on the other end surface of the pump cylinder for closing the other end opening surface of the cylinder chamber and slidingly contacting the tip end surface of the rotary shaft; an oil provided on the thrust plate and communicating with the lubricating oil in the oil sump portion A suction portion, a notch groove provided in a radial direction from an outer peripheral surface at a portion of the rotary shaft opposed to the cylinder chamber, displaceably engaged with the notch groove, and a centrifugal force acting along with rotation of the rotary shaft to rotate around the cylinder chamber. A roller pin for contacting the surface to divide the cylinder chamber, and for sucking the lubricating oil in the oil reservoir from the oil suction part into the cylinder chamber;
In the vicinity of the notch groove, and in the rotation direction forward of the notch groove.
In the radial direction from the circumference of the rotating shaft
Is, the pressure increase due to the decrease in the cylinder chamber volume, axial direction from the tip end surface of the rotary shaft so as to communicate with the discharge passage, and the discharge passage lubricating oil of the cylinder chamber pumping guide
And a lubrication oil passage that guides the lubricating oil fed from the oil discharge passage to the compression mechanism.

[0022]

[0023]

According to the present invention , in addition to the rotary shaft, only the seal plate, the pump cylinder, the thrust plate, the roller pin, and the like are required as essential components of the oil supply pump device. Is fine.

Since the cylinder chamber and the rotary shaft are eccentric, the rotary shaft is still eccentric with respect to the cylinder chamber, and the roller pin separates the cylinder chamber.
Exactly the same pumping action as in the past. Further , as the rotation shaft rotates at a higher speed, a strong centrifugal force is generated in the discharge passage, and the pressure in the cylinder chamber increases.

The lubricating oil in the cylinder chamber easily leaks from the sliding contact portion, and a sufficient amount of the lubricating oil cannot be guided from the oil discharge passage to the oil supply passage. That is, if the rotation speed is high, the oil supply efficiency is reduced, and there is no extreme decrease in the oil level.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows a scroll compressor used in, for example, a refrigerating apparatus.

In the figure, reference numeral 21 denotes a sealed case, in which a support frame 22 is provided.
Is rotatably supported. A compression mechanism 24, which will be described later, is provided above the rotating shaft 23, and an electric motor 27 including a stator 25 and a rotor 26 is provided below.

The compression mechanism section 24 includes a fixed scroll blade 28 attached to and fixed to the support frame 22 and an orbiting scroll blade 29 pivotally supported by an eccentric portion 23a at the upper end of the rotating shaft 23. Back pressure guide means 30 for applying gas pressure to the back side.

The fixed scroll wings 28 and the orbiting scroll wings 29 are both end plates 32, 33 and spiral wings 34, 33 provided integrally with the end plates 32, 33.
35. The wing portions 34 and 35 are meshed with each other, and a compression chamber S which is a spiral space surrounded by the end plate portions 32 and 33 is formed.

A concave portion 36 is provided at the center of the upper surface of the fixed scroll blade end plate portion 32, and a discharge port 37 communicating with the spiral center of the compression chamber S is provided through the end plate portion 33.

Further, on the upper surface side of the fixed scroll blade end plate portion 32, an annular concave portion 38 is provided around the discharge port 37, and an intermediate pressure introducing hole 39 communicating with the compression chamber S is opened here. .

On the upper surface side of the fixed scroll blade 29, a back pressure plate 40 for partitioning the inside of the sealed case 21 into an upper end space and a lower space is provided and fixed to the sealed case 21.
This back pressure plate 40 is provided with a check valve 41 at the center,
It communicates with the discharge port 37.

Further, the fixed scroll blades 29 are axially moved within a narrow gap with the back pressure plate 40 by the seal rings 42 and 43 provided along the inner peripheral portion and the outer peripheral portion of the concave portion 38. However, a reliable seal is provided. A discharge pipe 44 is connected to an upper side surface of the sealed case 21 and a portion communicating with the upper space of the back pressure plate 40, and communicates with a condenser (not shown) of the refrigerating device. The sealed case 21
A suction pipe 45 is connected to a lower side surface of the refrigeration apparatus, and communicates with an evaporator (not shown) of the refrigeration apparatus. On the other hand, the lower end of the rotating shaft 23 projects downward from the electric motor 27 and is rotatably supported by a sub-bearing 46 attached to the closed case 21.

An oil reservoir 47 for collecting lubricating oil is formed at the inner bottom of the closed case 21. The lower end of the rotary shaft 23 and an oil supply, which will be described later, provided at the end of the rotary shaft 23 will be described. The pump device P is immersed. Next, the refueling pump device P will be described with reference to FIGS.
The device main body 46 also serves as the auxiliary bearing, and pivotally supports a lower end portion, which is a tip end portion of the rotating shaft 23, via a metal 50. An oil supply passage 51, which is an oil supply hole, is provided from the lower end surface of the rotary shaft 23 to the compression mechanism 24 shown above and along the axial direction. At a position near the lower end of the oil supply passage 51, a discharge passage 52 formed of a lateral hole provided radially from the peripheral surface of the rotating shaft 23 is provided.

Further, a notch groove 53 is provided at the lower end of the rotating shaft 23 along the radial direction from the peripheral surface and in a range not reaching the oil supply passage 51. The cutout groove 53 is formed so as to have a completely parallel surface from the peripheral surface of the rotary shaft 23 to a halfway portion, and has a semicircular shape having a diameter corresponding to a distance between the parallel surfaces at a tip portion. .

A roller pin 54 is engaged with the notch groove 53. The axial length of the roller pin 54 matches the depth of the notch groove 53. The diameter of the roller pin 54 is extremely slightly smaller than the diameter of the semicircular portion formed at the end of the notch groove 53, and is therefore movable with respect to the groove 53.

The lower end of the rotating shaft 23 has a seal plate 5
5 and the pump cylinder 56 are engaged with each other. Further, both the seal plate 55 and the pump cylinder 56 are supported by the thrust plate 57. The thrust plate 57 is supported by a snap ring 58 provided on the apparatus main body 46 so that the lower end surface of the rotating shaft 23 is in sliding contact. The seal plate 55 has a ring shape with an equal diameter,
The rotation shaft 23 is inserted into and engaged with the inner diameter portion, and the outer diameter portion is equal to the outer diameter portion of the pump cylinder 56.

The thickness of the pump cylinder 56 is equal to the depth of the cutout groove 53 and the axial length of the slide pin 54. Inside, a cylinder port 56a having a center eccentric with the axis of the rotating shaft 23 and having a diameter larger than the diameter of the rotating shaft 23 is provided. In other words, the pump cylinder 56 is an eccentric ring.

An assembly is made so that a part of the peripheral surface of the rotating shaft 23 is in rolling contact with the cylinder port 56a. That is,
The cylinder port 56a is eccentric with respect to the axis of the rotating shaft 23,
And since it is larger than this diameter, this assembly is possible.

A seal plate 55 and a thrust plate 57 are overlapped on both upper and lower end surfaces of the pump cylinder 56, and the open portion of the cylinder port 56a is closed regardless of the rotation of the rotary shaft 23, thereby forming a closed space. You. This enclosed space,
Called cylinder chamber 60.

An oil suction notch 61 is provided in the periphery of the cylinder port 56a on the lower surface side of the pump cylinder 56, and is located at a position facing the cylinder chamber 60 in an assembled state.

The thrust plate 57 is provided with an oil suction portion 62 which is a long hole communicating with the oil suction notch portion 61.
The oil suction portion 62 opens into the lubricating oil in the oil sump 47.

In the scroll type compressor provided with the hot water supply pump device P constructed as described above, the electric motor 27
And the compression mechanism 24 is driven, the low-pressure refrigerant gas is guided from the suction pipe 45 through the evaporator, and fills the lower space from the back pressure plate 30 in the closed case 21.

This refrigerant gas is sucked into the outer peripheral portion of the compression chamber S formed by the orbiting scroll blades 28 and the fixed scroll blades 29, and is gradually transferred to the center with the orbital motion of the orbiting scroll blades 29. In addition, compression is performed by reducing the compression capacity. When the pressure has risen to the predetermined pressure,
The gas is discharged from the discharge port 37 to the space above the back pressure plate 40 via the check valve 41, and further guided to the condenser via the discharge pipe 44.

A part of the high-pressure refrigerant gas discharged from the discharge port 37 once fills the concave portion 36 and applies a back pressure to the central portion of the fixed scroll blade 29. On the other hand, an intermediate-pressure gas is introduced from the compression chamber S through the intermediate-pressure introducing hole 39 to the concave portion 38 serving as the intermediate-pressure chamber, where the gas is filled and filled in the fixed scroll blade 29.
Apply back pressure to the peripheral edge of.

As described above, in the normal operation state, the back pressure guide means 30 applies an effective back pressure to the fixed scroll blade 29, restricts the movement in the axial direction, and forms the orbiting scroll forming the compression chamber S. The clearance with the wing 28 is kept optimal.

If the pressure in the compression chamber S becomes abnormally high under some conditions, the pressure in the compression chamber S exceeds the back pressure of the back pressure guide means 30, and the fixed scroll blade 29 moves in the axial direction. The clearance of the compression chamber S with the orbiting scroll blade 28 is increased, and the abnormally high pressure gas in the compression chamber S is released into the sealed case 21. The scroll wings 34 and 35 exhibit a so-called compliance function in which stress on the scroll wings 34 and 35 is eliminated.

On the other hand, in the refueling pump device P, the rotating shaft 23 rotates in a state of being in rolling contact with a part of the peripheral surface of the cylinder chamber 60. With this rotation, the roller pin 54
The roller pin 54 rotates (revolves) with the rotating shaft 23 in a state in which the roller pin 54 is always in rolling contact with the peripheral surface of the cylinder chamber 60. Except when the roller pin 54 coincides with the rolling contact portion between the rotating shaft 23 and the peripheral surface of the cylinder chamber 60,
The roller pin 54 divides the cylinder chamber 60 into two.

To be more specific, in the state shown in FIG. 3 (a), the roller pin 54 has just passed through the suction notch 61, and the cylinder chamber 60 between the roller pin 54 and the roller pin 54 has a negative pressure. As a result, the lubricating oil in the oil sump 47 is supplied to the cylinder chamber 60 through the oil suction 62.
Inhale.

The lubricating oil has already been sucked into the cylinder chamber 60 which is sectioned on the rotation direction side of the roller pin 54, and is partially compressed from the discharge passage 52 through the oil supply passage 51 while being compressed to some extent. Thus, oil is supplied to the compression mechanism 24.

When the rotating shaft 23 rotates clockwise from the position (a) in the figure to the position (b), the capacity of the cylinder chamber 60 communicating with the suction notch 61 increases. And more lubricating oil is stored in the oil sump 47.
Inhale from. On the other hand, in the cylinder chamber 60 on the rotation direction side, the capacity is further reduced, and the amount of lubricating oil fed to the discharge passage 52 is increased.

As shown in (c), at the position further displaced by 90 °, the cylinder chamber 6 communicating with the suction notch 61 is moved.
The capacity of the zero portion is further increased and the lubricating oil is continuously sucked. The capacity of the cylinder chamber 60 on the rotation direction side is almost zero, and almost no lubricating oil is discharged to the discharge passage 52.

As shown in (d), at the position further displaced by 90 °, the rolling contact portion of the roller pin 54 with the peripheral surface of the cylinder chamber 60 coincides with the rolling contact portion of the rotary shaft 23 with the peripheral surface of the cylinder chamber 60. , And all the cylinder chambers 60 communicating with the suction notch 61 are included. On the other hand, the suction notch 61 and the discharge passage 52 communicate with each other, and there is no lubricating oil discharged from the discharge passage 52. Then, return to the state of (a) again,
The above-described refueling action is repeated. In this manner, the refueling pump device P normally performs an extremely efficient refueling operation.

However, in order to increase the circulation amount of the refrigerant, the compressor may be operated at a higher rotation speed. The refueling pump device P in this case reduces the refueling efficiency with an increase in the number of revolutions, and suppresses a sharp increase in the discharge amount. That is, the discharge passage 52 provided in the rotating shaft 23
Is provided radially from the peripheral surface of the rotating shaft 23 and communicates with the oil supply passage 51. Due to the configuration of the discharge passage 52, as the rotating shaft 23 rotates at a higher speed, a stronger centrifugal force is generated in the lubricating oil in the discharge passage 52.

Originally, the lubricating oil in the discharge passage 52 is pressure-fed from the peripheral surface of the rotary shaft 23 toward the oil supply passage 51 on the shaft center side by a pump action, but this time due to the effect of the centrifugal force. The pressure in the cylinder chamber 60 is increased, and it is easy to leak from the abutting portion of the component.

For example, the rolling contact portion of the rotary shaft 23 and the rolling contact portion of the roller pin 54 with respect to the peripheral surface of the cylinder chamber 60,
It easily leaks from the peripheral surface and the upper and lower end surfaces of the roller pin 54 with respect to the notch groove 53, and the overlapping surface of the seal plate 55 and the thrust plate 57 with respect to the upper and lower end surfaces of the pump cylinder 56.

Therefore, by suppressing an excessive amount of oil supply at the time of high-speed rotation of the rotary shaft 23, the oil supply pump device P of the present invention is controlled by the amount of oil flowing out to the refrigeration cycle, as shown by the change A in FIG. The increase rate of a certain pump oil discharge amount is reduced.

On the other hand, in the oil supply pump device having the conventional structure, as shown by the change B in the figure, the oil discharge amount increases linearly with the increase in the rotational speed. It will cause occurrence. Then, the discharge passage 52 is connected to the notch groove 5.
3 and a position forward of the notch groove 53 in the rotation direction.
Through the discharge passage 52 until the end of one rotation.
To discharge the lubricating oil.
It is possible to increase the amount of refueling during turning.

Although the scroll type compressor has been described as the hermetic compressor, it is not necessarily limited to a compressor having this type of compression system. It can also be used for compressors that compress other types of compressed gas or air.

[0060]

As described above, according to the present invention ,

A pump cylinder having a cylinder chamber that is eccentric with respect to the axis of the rotary shaft, a seal plate that closes one end opening surface of the cylinder chamber, and a rotary shaft tip surface that closes the other end opening surface of the pump cylinder. The sliding contact thrust plate and roller pins are the components of the lubrication pump device, and are structurally simpler with fewer parts, improving workability and assemblability, and ensuring reliable lubrication. This has the effect of improving the refueling efficiency. Further , according to the present invention , the discharge passage is rotated near the notch groove and more than the notch groove.
At the position in front of the rolling direction,
The rotation shaft is provided so that the oil supply passage communicates with the discharge passage.
Since it was provided along the axial direction from the end face of the tip of

When the rotating shaft rotates at a high speed, a strong centrifugal force is generated in the discharge passage to increase the pressure in the cylinder chamber to change the state to a state in which the cylinder chamber easily leaks from the sliding contact portion. This has the effect of reducing the oil level and the amount of oil discharged to the outside to improve reliability. And the discharge
The path is located near the notch groove and ahead of the notch groove in the rotational direction.
Through the discharge passage until the end of one revolution
To discharge the lubricating oil when the rotating shaft rotates at low speed.
The effect is that the amount of refueling can be increased.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll compressor, showing one embodiment of the present invention.

FIG. 2A is a vertical cross-sectional view of the oil supply pump device of the embodiment. (B) is an exploded perspective view of the oil supply pump device of the embodiment.

FIG. 3 is a view for sequentially explaining a pump action of the embodiment.

FIG. 4 is a diagram comparing the lubrication characteristics of a pump device of the present invention and a pump device having a conventional structure.

FIG. 5A is a longitudinal sectional view of a refueling pump device showing a conventional example of the present invention. (B) is an exploded perspective view of the oil supply pump device of the conventional example.

[Explanation of symbols]

23 ... rotating shaft, 27 ... electric motor part, 24 ... compression mechanism part, 2
1 ... closed case, 47 ... oil reservoir, 60 ... cylinder chamber,
Reference numeral 56 denotes a pump cylinder, 55 denotes a seal plate, 57 denotes a thrust plate, 62 denotes an oil suction portion, 53 denotes a cutout groove, 54 denotes a roller pin, 52 denotes a discharge passage, and 51 denotes an oil supply passage.

Claims (1)

(57) [Claims] An oil supply pump device for a compressor in which an electric motor unit and a compression mechanism unit connected via a rotating shaft are housed in a closed case, provided at an end of the rotating shaft and rotating. A pump cylinder having a cylinder chamber formed eccentrically with respect to the axis of the rotary shaft so that a part of the peripheral surface of the rotary shaft is always in rolling contact with a fixed portion; and the cylinder chamber provided on one end surface of the pump cylinder. A seal plate provided on the other end surface of the pump cylinder, for closing the other end surface of the cylinder chamber and slidingly contacting the tip end surface of the rotating shaft; , with the lubricating oil in the oil reservoir section
An oil suction portion that passes therethrough; a notch groove provided in a radial direction from an outer peripheral surface at a portion of the rotation shaft facing the cylinder chamber; a centrifugally displaceably engaged with the notch groove and acting with rotation of the rotation shaft. A roller pin that abuts the cylinder chamber peripheral surface by force to separate the cylinder chamber, and allows the lubricating oil in the oil sump to be sucked into the cylinder chamber from the oil suction section , and near the notch groove and rotated more than the notch groove Direction forward
In the radial direction from the circumference of the rotating shaft
When the pressure rises due to the decrease in the capacity of the cylinder chamber, the discharge passage for guiding the lubricating oil in the cylinder chamber is guided, and the end face of the end of the rotary shaft is communicated with the discharge passage .
An oil supply passage provided along the axial direction from the oil discharge passage for guiding the lubricating oil fed from the oil discharge passage to the compression mechanism.