JPH0468475B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a refueling pump device for a compressor that can be operated under inverter control, and more specifically, a refueling pump device that is attached to the shaft end of a drive shaft that drives a compression element. The present invention relates to an oil supply pump device for a compressor that supplies lubricating oil to an oil supply passage provided in a shaft.

(Prior Art) A conventional oil supply pump device for a compressor of this type is described in, for example, Japanese Patent Application Laid-Open No. 60-73083, and
As shown in the figure, a compression element and a motor 3 are housed inside a sealed casing 1, and the motor 3 and the compression element are interlocked and connected via a drive shaft 4, and an oil supply extending in the axial direction of the drive shaft 4 is provided. While forming a passage 41, a centrifugal pump P facing the bottom oil reservoir 1a of the casing 1 is attached to the lower end of the drive shaft 4, and as the drive shaft 4 is driven to rotate, the centrifugal pump P , the lubricating oil in the oil reservoir 1a is pumped up to the oil supply passage 41, and from this oil supply passage 41, the lubricating oil is supplied to the bearing part of the drive shaft 4, the bearing part of the compression element, and other lubricating parts. I'm trying to refuel.

(Problems to be Solved by the Invention) However, in the conventional compressor described above, since a centrifugal pump P is used to supply oil to each of the lubrication points, the following problems occur.

That is, since the amount of lubricating oil supplied by the centrifugal pump P is proportional to the square of the frequency applied to the motor 3 during the inverter-controlled operation of the compressor, the amount of lubricating oil supplied by the centrifugal pump P when the compressor is driven is As shown by the dotted line curve shown as a reference example in FIG. 9, the oil supply ratio increases quadratically as the frequency of the motor 3 increases.

Therefore, when the compressor is operated under inverter control,
When the motor 3 is operated in a high frequency range, the amount of oil supplied by the centrifugal pump P increases significantly, causing excessive oil supply to each of the lubricating points, and refrigerant gas discharged from the compressor due to excessive oil supply. The amount of lubricating oil mixed into the casing 1 increases, causing a problem of oil drainage, and furthermore, as the amount of oil supplied increases, the amount of lubricating oil in the oil reservoir 1a in the casing 1 becomes insufficient. It is. Furthermore, when the motor 3 is operated at a low frequency, the amount of oil supplied by the centrifugal pump P may be insufficient, resulting in poor lubrication at each of the lubrication points.

The present invention was developed in view of the above-mentioned problems, and its purpose is to prevent excessive lubrication during operation in a high frequency range by providing a constant displacement pump function in which the lubrication amount is linearly increased or decreased in direct proportion to the frequency. A compressor lubrication pump that does not drip, can reliably supply lubrication in the low frequency range, and can improve assembly work efficiency without causing assembly errors of component parts. The goal is to provide equipment.

(Means for Solving the Problems) As shown in the embodiments of the drawings, the configuration of the present invention is such that the oil supply passage is attached to the shaft end of the drive shaft 4 that drives the compression element 2 and is provided in the drive shaft 4. 41 is a compressor oil supply pump device for supplying lubricating oil to a compressor. A cylindrical rotor 54 having a suction port 54b is attached to the rotor 54, and a yoke 52 that fits on the outer circumference of the rotor 54 and forms a pump chamber 52a inside is bolted to the lower surface of the rotor 54. The pump chamber 52 receives the yoke 52.
A pair of bolt holes 55a are provided in the closing plate 55 at symmetrical positions with respect to the axis of the drive shaft 4.
55a, and the bolt holes 55a, 55
perpendicular to the straight line connecting a, and the drive shaft 4
The rotor 54 is placed at a symmetrical position about the axis of the rotor 54.
A pair of oil intake holes 5 with long holes corresponding to the eccentricity multiple of
5b and 55b, and the bolt hole 55
This is characterized in that the spacing between the oil intake holes 55a and 55a is different from the spacing between the oil intake holes 55b and 55b.

(Function) However, in the above-mentioned oil supply pump device, the shaft end of the drive shaft 4 has an eccentric shaft portion that is eccentric with respect to the axial center of the drive shaft 4, and the eccentric shaft portion has a suction port 5.
A rotor 54 having a pump chamber 52a and a discharge port is attached, and a yoke 52 having a pump chamber 52a is provided on the outer circumference of the eccentric shaft portion of the rotor 54.
By eccentrically rotating the rotor 54 within the pump chamber 52a of the yoke 52 as the drive shaft 4 is rotationally driven, a constant amount of oil supply corresponding to the rotational speed of the rotor 54, that is, the drive shaft 4 can be obtained. It is.

Further, the closing plate 55, which is bolted to the rotor 54 in order to receive and support the yoke 52 and close the pump chamber 52a of the rotor 54, includes:
A pair of bolt holes 55a are formed at symmetrical positions with respect to the axis of the drive shaft 4, and are perpendicular to the straight line connecting the bolt holes 55a, and with the center of the axis of the drive shaft 4 as the center. A pair of oil intake holes 55b having a long hole shape corresponding to the eccentricity multiple of the rotor 54 are formed at symmetrical positions, and the intervals between each bolt hole 55a and each oil intake hole 55b are Since the intervals are different, when bolting the closing plate 55 to the rotor 54,
This prevents the bolt hole 55a from being mistaken for the oil intake hole 55b, and even if the closing plate 5
5 is turned inside out, the closing plate 55 is attached to the rotor 5.
4 can be reliably assembled, and the assembly work efficiency can be improved.

(Example) A pump device for a compressor according to the present invention will be described below with reference to the drawings and an example.

FIG. 10 shows the overall structure of a scroll compressor, in which there are
An upper frame 11 and a lower frame 12 are respectively assembled, and the upper frame 11 supports the compression element 2 consisting of a fixed scroll 21 and a revolving scroll 22. While supporting a motor 3 whose rotational speed is variable through conversion, this motor 3 and the compression element 2 are interlocked and connected by a drive shaft 4' supported by bearings on each of the frames 11 and 12.
Due to the rotation of the drive shaft 4 accompanying the drive of the
1, and these both scrolls 2
The refrigerant gas is compressed between 1 and 22.

Further, a refueling pump device 5 facing the bottom oil sump 1a of the casing 1 is attached to the lower end of the drive shaft 4, and the oil sump 1a is connected to the bottom end of the drive shaft 4 via the oil pump device 5.
The lubricating oil inside is pumped up to an oil supply passage 41 formed vertically penetrating inside the drive shaft 4, and from the oil supply passage 41 to the bearing locations of the drive shaft 4 and each of the frames 11 and 12, and the drive shaft 4. The lubricating oil is supplied to bearing locations of the shaft 4 and the revolving scroll 22 and other lubricating locations.

Therefore, the oil supply pump device 5 used in the above compressor is of a constant displacement type in which the amount of oil supply increases or decreases linearly in direct proportion to the frequency of the motor 3, that is, the rotation speed of the drive shaft 4. be.

As shown in detail in FIGS. 1 and 2, the oil supply pump device 5 includes a pump housing 51 fixedly supported on the lower end surface of the lower frame 12 via fixing bolts B, and a pump chamber having an oval shape. 52a
A yoke 52 is supported by the pump housing 51 to freely reciprocate only in the short diameter direction, and a pump chamber 52a of the yoke 52 is fixed to a position below the shaft end of the drive shaft 4 via a connecting cylinder 53. A rotor 54 having a cylindrical shape that is rotated eccentrically at the rotor 54, and a closing plate 55 having a disc shape fixed to the lower surface side of the rotor 54 with fixing bolts B so as to stop the yoke 52 and close the pump chamber 52a. It consists of

As is clear from FIG. 3, the housing 51 is integrally provided with a mounting piece 51b extending radially outward at the upper end of the cylindrical body 51a, and the mounting piece 51b' is fixed to the lower frame 12. The cylindrical body 51 is fixed through bolts B, and
Extension pieces 51c, 51c extending downward are formed facing each other in a, and a guide groove 51d is provided at the lower end of each extension piece 51c.

Furthermore, as is clear from FIG. 4, the yoke 52 has semicircular portions on both sides in the lateral direction, and the yoke 52 has a horizontally long elliptical shape formed by connecting the semicircular portions with a straight portion. In addition to forming a pump chamber 52a, supporting pieces 52b, 52b are integrally provided on the outer circumference of the yoke 52 in the short diameter direction of the pump chamber 52a, that is, in the vertical direction in the figure. A guide groove 51 in which a support piece 52b is provided in each extension piece 51b of the housing 51.
d, so that the yoke 52 is reciprocated only in the short diameter direction of the pump chamber 52a by the respective guide grooves 51d.

As is clear from FIGS. 5 and 6, the rotor 54 is integrally formed with an eccentric portion 54a eccentric to the axis of the drive shaft 4 at its lower end, and the eccentric portion 54a is connected to the yoke. 52 pump chambers 52a
By rotating the eccentric part 54a eccentrically within the pump chamber 52a, the eccentric part 54a is rotated eccentrically within the pump chamber 52a while moving the yoke 52 in the short diameter direction of the pump chamber 52a.
The lubricating oil is sucked and compressed by reciprocating in the long diameter direction of the eccentric part 54a, and a suction port 54b is opened at a position concentric with the axis of the eccentric part 54a on the lower surface side of the eccentric part 54a. Eccentric part 54a
A discharge port 54c is opened on the outer peripheral surface side of the rotor 54, and a suction passage 54d that communicates with the suction port 54b and extends radially outward from the inside of the rotor 54;
c, a discharge passage 54e that extends from the bottom to the top in an inverted conical shape and opens into the oil supply passage 41 of the drive shaft 4 is formed.

Further, as shown in FIG. 7, the closing plate 55 has an outer diameter corresponding to the pump chamber 52a of the yoke 52.
A pair of bolt holes 5 are formed in the closing plate 55 at vertically symmetrical positions with respect to the axis of the drive shaft 4.
5a, 55a are formed through each bolt hole 5.
The closing plate 55 is integrally assembled to the rotor 54 by screwing fixing bolts B from 5a to each attachment hole 54g provided on the lower surface side of the rotor 54, and the closing plate 55 is used to attach the yoke 52. The lower surface of the rotor 54 is received and supported by the housing 51, and the rotor 54 is perpendicular to the straight line connecting the bolt holes 55a and symmetrically centered on the axis of the drive shaft 4. A pair of oil intake holes 55b, 5 with a long hole shape corresponding to the eccentricity multiple.
5b, while each of these oil intake holes 55
The distances between the bolt holes 55a and the bolt holes 55a are set to be different.

Specifically, as shown in the figure, the distance between the centers of each bolt hole 55a is set as D1,
In addition, when the distance between the centers of each of the oil intake holes 55b is D2, the holes are formed so that the relationship D1≠D2 holds, and by doing so, when the closing plate 55 is assembled to the rotor 54, The bolt hole 55a of the closing plate 55 is connected to the rotor 54.
The oil intake hole 55b does not face the suction port 54b of the rotor 54, and the oil intake hole 55b does not face the attachment hole 5 of the rotor 54.
4g, that is, it is no longer possible to confuse the bolt hole 55a and the oil intake hole 55b, and the rotor 5 of the closing plate 55
Therefore, it is possible to improve the assembly work efficiency for 4.

Also, each oil intake hole 55 formed in the closing plate 55
b is formed in the shape of a long hole on the same circumferential line as the suction port 54b provided on the eccentric portion 54a of the rotor 54, with a predetermined multiple of the eccentricity between the suction port 54b and the axial center of the drive shaft 4. It is,
In this way, when assembling the closing plate 55 to the rotor 54, even if the closing plate 55 is turned upside down or wrong, the closing plate 55 can be reliably assembled to the rotor 54.

Next, the operation of the oil supply pump device 5 configured as above will be explained based on FIG. 8.

First, as shown in A of the figure, the rotor 54
is rotated in the direction of the arrow so that the cylinder 52 is located at the lowest position, the rotor 54
An eccentric portion 54a is located at an intermediate portion of the pump chamber 52a in the yoke 52.
A right chamber A and a left chamber B, each having a predetermined size, are formed on both sides of the pump chamber 52a in the lateral direction with the pump chamber 4a as the center, and lubricating oil is supplied to the right chamber A from the suction port 54b through the suction passage 54d. supplied,
Further, the left ventricle B is connected to the oil supply passage 41 of the drive shaft 4 via the discharge port 54c and the discharge passage 54e.
The lubricating oil is discharged from the left ventricle B to the oil supply passage 41. Therefore, in the case of FIG. The chamber is in the process of discharging lubricating oil.

After this, as shown in FIG. B, when the yoke 52 is moved upward from the lowermost position by the rotation of the rotor 54, the left ventricle B of the pump chamber 52a is blocked by the eccentric portion 54a of the rotor 54. , and the right ventricle A becomes larger, so that the left ventricle B has completed discharging the lubricating oil, and the right ventricle A has completed suctioning the lubricating oil.

Furthermore, as shown in FIGS. B to C, when the yoke 52 is positioned at the uppermost position due to the rotation of the rotor 54, the eccentric portion 54a of the rotor 54 is located in the middle of the pump chamber 52a in the yoke 52. The suction port 54b communicates with the left ventricle B, and the right ventricle B communicates with the discharge port 54c. Therefore, in the case of Figure C, the left ventricle B is lubricated. While the oil is being sucked in, the right ventricle is also in the middle of discharging lubricating oil.

Further, as shown in FIGS. C to D, when the yoke 52 is moved downward from the uppermost position due to the rotation of the rotor 54, the eccentric portion 54a of the rotor 54 causes the pump chamber 52a to
The right ventricle A is occluded, and the left ventricle B becomes large, so that the right ventricle A has completed discharging the lubricating oil, and the left ventricle B has completed suctioning the lubricating oil.

As explained above, the eccentric portion 54a of the rotor 54 is eccentrically rotated within the pump chamber 52a of the yoke 52, so that each rotation of the rotor 54, that is, the drive shaft 4, causes the left and right chambers to rotate.
The suction and discharge of lubricating oil are repeated in step B, resulting in constant capacity operation.

Next, the oil supply characteristic graph shown in FIG. 9 will be explained. This figure shows frequency (Hz) on the horizontal axis,
The graph shows a refueling characteristic graph in which the vertical axis represents the refueling amount ratio with the refueling amount set to 1 during operation at 30 (Hz).
The compressor is normally operated under inverter control in the range of 30 to 120 (Hz), so even when operating at 30 (Hz), the minimum amount of lubricating oil required at the lubricating points is Said 30 to supply the amount
The amount of oil supplied is set based on (Hz).

As is clear from Figure 9 above, in the conventional system, the amount of oil supplied increases quadratically from the low frequency range to the high frequency range, as shown by the dotted line graph in the same figure, and excessive oil supply occurs when operating in the high frequency range. However, in the case of the present invention, as shown by the solid line graph in the same figure, the amount of refueling increases linearly from the low frequency range to the high frequency range.
Therefore, even when operating in a high frequency range, the necessary predetermined amount of oil is supplied without excessive oil supply.

(Effects of the Invention) As explained above, in the compressor oil supply pump device according to the present invention, the shaft end of the drive shaft 4 that drives the compression element 2 has an axial center that is eccentric to the axial center of the drive shaft 4. , a suction port 54 is located concentrically with this axis.
At the same time as attaching the rotor 54 provided with the
A yoke 52 that forms a yoke 52 and a closing plate 55 that is bolted to the lower surface of the rotor 54 and receives the yoke 52 to close the pump chamber 52a. A pair of bolt holes 55 are located symmetrically around the center.
a, 55a, and the bolt holes 55a, 5
5a, and the drive shaft 4
The rotor 54 is placed at a symmetrical position about the axis of the rotor 54.
A pair of oil intake holes 5 with long holes corresponding to the eccentricity multiple of
5b, 55b, and each of the bolt holes 5
5a and each oil intake hole 55b are formed at different intervals, it is possible to obtain a constant amount of oil supply corresponding to the rotational speed of the rotor 54, that is, the drive shaft 4, and moreover. When bolting the closing plate 55 to the rotor 54, it is possible to prevent the bolt hole 55a from being mistaken for the oil intake hole 55b, and even if the closing plate 55
The closing plate 55 is attached to the rotor 54 even when the
As a result, the assembly can be reliably assembled, and the assembly work efficiency has been significantly improved.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing the main parts of the oil supply pump device according to the present invention, FIG. 2 is a bottom view of the same, FIG. 3 is a sectional view of the pump housing, FIG. 4 is a plan view of the yoke, and FIG. 6 is a bottom view of the rotor, FIG. 7 is a plan view of the closing plate, FIG. 8 is a drawing explaining the operating state of the oil supply pump device, FIG. 9 is a graph showing the oil supply characteristics, and FIG. Figure 10 is a longitudinal cross-sectional view showing the overall structure of the compressor equipped with the same oil supply pump chamber.
FIG. 1 is a drawing showing a conventional example. 2...Compression element, 3...Motor, 4...Drive shaft, 41...Oil supply passage, 52...Yoke, 52a
... Pump chamber, 54 ... Rotor, 54b ... Suction port, 55 ... Closing plate, 55a ... Bolt hole,
55b...Oil intake hole.

Claims (1)

[Claims] 1 A compressor oil supply pump device that is attached to the shaft end of a drive shaft 4 that drives a compression element 2 and supplies lubricating oil to an oil supply passage 41 provided in the drive shaft 4, A cylindrical rotor 54 having an axis eccentric to the axis of the drive shaft 4 and having a suction port 54b concentrically with the axis is attached to the shaft end, and is fitted onto the outer periphery of the rotor 54. A yoke 52 that fits together and forms a pump chamber 52a therein is bolted to the lower surface of the rotor 54 to receive the yoke 52 and form a pump chamber 52a.
A pair of bolt holes 55a are provided in the closing plate 55 at symmetrical positions with respect to the axis of the drive shaft 4.
55a, and the bolt holes 55a, 55
perpendicular to the straight line connecting a, and the drive shaft 4
The rotor 54 is placed at a symmetrical position about the axis of the rotor 54.
A pair of oil intake holes 5 with long holes corresponding to the eccentricity multiple of
5b and 55b, and the bolt hole 55
An oil supply pump device for a compressor, characterized in that the distance between the holes 55a and 55a is different from the distance between the oil intake holes 55b and 55b.