JP2000087856A - Closed type electrically driven compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently secure performance of a lubrication pump even with a rotary shaft of a comparatively small diameter by attaching the lubrication pump in a cylindrical bore formed on a lower end of the rotary shaft and forming an oblique passage and a spiral passage so as to be communicated with the cylindrical bore. SOLUTION: In a closed type electrically driven compressor 1, a compressor unit composed of an electrically driven motor 3, a compression mechanism 4, and a block 5 for integrating them is housed in a closed casing 2. In such a compressor 1, a large end of a connecting rod 10 is connected to an eccentric shaft 9 on an upper end of a rotary shaft 7 pivoted to a bearing 8 of the block 5. A piston 13 is connected to a small end by means of a piston pin 11. An oil supply pump 17 is press-fitted and connected to a cylindrical bore 18 of a small-diameter formed on a lower end of the rotary shaft 7. An oblique passage 19 extended obliquely upward from the upper end of the cylindrical bore 18 is formed on the rotary shaft 7. A spiral groove 20 is formed so as to be communicated with the upper end of the oblique passage 19. An upper end of the spiral groove 20 is communicated with an eccentric passage 23 in the eccentric shaft 9.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for use in a freezing / refrigeration apparatus, and more particularly, to a compressor in which oil stored in a casing is stored in a rotary sliding portion of the compressor using a rotary shaft. Related to lubrication systems.
The present invention relates to how to make a compressor that can efficiently pump a large amount of oil on a relatively small-diameter rotary shaft.

[0002]

2. Description of the Related Art Many pump systems for lubricating oil for compressors have been proposed so far. To save energy, the diameter of the rotary shaft is set small to reduce sliding loss. Then, the centrifugal force for pumping up the oil is reduced, so that a problem arises in that the required head and the amount of oil are reduced. This problem becomes even more problematic when low-viscosity oil is used to obtain a low input, from the viewpoint of heat generation of the rotary sliding portion and cooling of the oil itself. The conventional technique will be described below.

Conventionally, as a configuration of such a refrigerant compressor, there is Japanese Patent Publication No. 62-44108 shown in FIG. It was filed on January 23, 1980, and filed on August 19, 1981.
It will be described with reference to FIG. The compressor body a is housed in a closed container b,
An electric motor d is arranged at a lower part, and a compression mechanism e is arranged at an upper part with the frame c as a core. f denotes a rotating shaft, which is inserted through a bearing g of a frame c, and an outer diameter portion is fixed to a rotor h of a motor d, while a compression mechanism e is provided with a slider of a piston j via an eccentric shaft i. and engages in a known compression operation.

[0004] Inside the rotating shaft f, a slanted hole 1 having a relatively smaller diameter than the lower end thereof extends to the vicinity of the lower end of the bearing g, and is opened to the outer periphery of the rotating shaft f by a lateral hole m.
A spiral groove n is formed in a portion of the rotating shaft f located in the bearing portion g, and a lower end thereof communicates with the lateral hole m, and an upper end thereof has
The lower end of the vertical hole o provided in the eccentric shaft i is the thrust bearing sliding surface p.
And in other words, a part of the hole is directly opened on the surface of the rotating shaft so as to cross the horizontal hole q at the same time.

As another conventional example, as shown in FIG. 9, in Japanese Patent Publication No. 1-47632, a relatively large-diameter cylindrical hole s concentric with the rotation axis r is formed, and the vicinity of the upper end of the cylindrical hole is formed. A pump system is disclosed in which a spiral groove t located in a bearing portion communicates with a lateral hole u, and a cone-shaped pump member v is fixed below a rotation shaft.

Further, as another conventional example, as shown in FIG. 10, Japanese Utility Model Publication No. Sho 51-19204 discloses that a cone-shaped pump member w is arranged at the lower end of a rotating shaft and a bore for inserting the pump member. An inclined hole y having a smaller diameter than the peripheral edge of the upper end of x is continuously provided, and the inclined hole y is continuously connected to a spiral groove (not shown) located in the bearing portion.

[0007]

However, in the first conventional example, from the viewpoint of the amount of oil of the oil supply pump, the oil in the inclined hole 1 extending obliquely upward from the lower end directly is the oil in the oil sump. At a position slightly above the surface, the oil is immediately deflected only by the centrifugal force to the outer peripheral side of the inner surface of the inclined hole l, so that the oil is good in terms of the rising force, but inferior in terms of the amount of oil. is there.

In the second prior art, in order to raise the head of the centrifugal pump, it is necessary to increase the diameter of the cylindrical hole s. As the loss increases, the rotating shaft with low sliding loss, that is,
This is disadvantageous when a smaller diameter rotary shaft is used.

Furthermore, in the third prior art, a cylindrical cone-shaped pump member w and a small-diameter inclined hole y are combined, but when oil flows from the pump member w into the inclined hole y, the inclined hole y Since the opening range exists only on one side from the center of the cylindrical hole, the capacity of the cylindrical pump was not sufficiently transmitted to the inclined hole, and the oil amount was not sufficient.

[0010] In order to eliminate the conventional problems, the present invention can obtain a sufficient head and oil amount even if a low-loss oil having a relatively small diameter and low viscosity is used for energy saving. It is another object of the present invention to obtain a pump system which has good workability and does not easily cause variations in assembly.

[0011]

SUMMARY OF THE INVENTION The present invention provides a block having a compression mechanism in an airtight container, an electric motor disposed below the block, and a rotatable mounting provided on a bearing of the block. A rotating shaft having a relatively small diameter, and an eccentric shaft with which a connecting rod that operates a piston in a cylinder is engaged above a bearing of the rotating shaft, and a refueling pump smaller in diameter than the rotating shaft is provided with a rotating shaft of the rotating shaft. It is supported in a cylindrical bore formed at the lower end. At the upper end of the cylindrical bore, a lower end is opened so as to include the center, and an inclined passage is provided so that the upper end reaches below the bearing, and is inclined outward from below to above. A spiral groove is formed on the outer peripheral surface of the rotating shaft located on the inner surface of the bearing, and a lower end of the spiral groove communicates with a lower horizontal hole crossing the inclined passage, and an upper end of the spiral groove is provided on an eccentric shaft. Connected directly in the passage or in the upper side passage,
Further, an oil supply pump is provided continuously in the cylindrical bore.

In the fuel pump, a divider is inserted and locked, and a space without a divider is provided between the upper end of the cylindrical bore into which the fuel pump is inserted and fitted and the lower end of the divider.

The divider has a vertically symmetric shape,
A substantially half-moon-shaped notch is provided substantially at the center of the end. Also, the width in the longitudinal direction, which is also near the center, is slightly larger than the end portion to form a press-fit portion, which is press-fitted and fixed in the refueling pump.

In such a configuration, the oil in the oil supply pump and the cylindrical bore forms a well-known parabolic free surface due to centrifugal force, and the oil covers the entire circumference of the cylindrical bore. Then, from the upper end of the cylindrical bore to the inclined passage, the oil flows toward the outer peripheral side near the outer surface of the rotating shaft as viewed from the inclined passage axis. At this time, the oil on the side opposite to the slope in the cylinder pump flows along the slope and flows into the outer peripheral side at the same time.

Further, by forming a space above the divider, the relative angle dependence of the insertion angle of the divider and the inclined passage is reduced.

[0016] Further, even if the lower end of the divider is deviated from the center of the inlet hole of the refueling pump, the opening ratio of the two divided inlets of the inlet hole can be increased even if the lower end of the divider is deviated from the center of the inlet hole. Will not change.

Further, by increasing the width near the center in the longitudinal direction, there is no insertion pressure direction of the divider, and the curvature of the divider is extremely small, so that the assembling can be performed.

[0018]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing an embodiment of the present invention.

Reference numeral 1 denotes a hermetic electric compressor in which a compressor unit 6 in which an electric motor 3 and a compression mechanism 4 are integrated in a block 5 is housed in an upper and lower hermetic container 2. Reference numeral 7 denotes a rotating shaft pivoted on the bearing 8 of the block 5 and has a relatively small diameter (for example, about 16 mm in diameter). The large end of the connecting rod 10 is connected to the eccentric shaft 9 at the upper end, and the small end is connected to the small end. Piston 1 sliding in cylinder 12 by piston pin 11
3 are connected. Reference numeral 14 denotes a valve plate having a suction hole, a suction valve, a discharge hole, and a discharge valve (none of which is shown). Reference numeral 15 denotes a cylinder head having a suction chamber and a discharge chamber (both not shown) defined therein. Reference numeral 16 denotes a suction muffler.

Reference numeral 17 denotes an oil supply pump fixed to a cylindrical bore 18 having a smaller diameter (for example, about 8 to 10 mm) than the rotary shaft 7 provided at the lower end of the rotary shaft 7. Reference numeral 19 denotes an inclined passage extending obliquely upward from the upper end of the cylindrical bore 18 and having a diameter slightly smaller than the cylindrical bore 18 (for example, about 5 to 8 mm) so that the center of the cylindrical bore 18 is included in the inner diameter. And one side is located as close as inscribed in the cylindrical bore 18. Further, the upper end is arranged so as to reach below the bearing 8 and to approach the outer peripheral surface of the rotating shaft 7. 20
Is a spiral groove, and the inclined passage 19 is formed in the lower horizontal hole 21.
Communicate with The upper end of the spiral groove 20 communicates with an eccentric passage 23 in the eccentric shaft 9 through an upper lateral hole 24.

Reference numeral 25 denotes a gas vent passage, which is opened on the outer peripheral surface in the direction opposite to the inclination of the inclined passage 19.

Reference numeral 26 denotes a divider made of a thin plate which is press-fitted and fixed in the oil supply pump 17 and has a substantially half-moon-shaped notch 27 at the upper and lower ends, and is formed vertically symmetrically so that there is no vertical direction. Reference numeral 28 denotes a press-fit portion formed at a substantially intermediate position and slightly widened. Reference numeral 29 denotes an inlet hole provided at the center of the bottom of the refueling pump 17.

Next, the behavior of the oil will be described with reference to FIGS. The rotation of the rotating shaft 7 causes the refueling pump 1
The rise of the oil 30 is formed in the whole of the inner peripheral wall in the inside 7. The oil in the portion A directly flows into the inclined passage 19, and the oil in the portion B on the side opposite to the portion A flows from the partially inverted conical surface of the cylindrical bore 18 as indicated by the arrow C.
And merges with the flow D on the outer peripheral wall side of the inclined passage 19. That is, as compared with the conventional pump, it functions to create a flow to the inclined passage 19 from the entire inner circumference in the oil supply pump 17.

FIG. 7 shows data obtained by measuring the correlation between the number of revolutions and the amount of lubrication of the rotating shaft of the conventional and the present invention using the rotating shafts having the same diameter performed by the present inventors. Yes, Figure 8
The conventional example 1 shown in FIG. 9, the conventional example 2 shown in FIG. 9, and the product of the present invention are all excellent in the present invention. In the model of FIG. 10, since the lower end of the inclined passage is opened only to one side,
It is considered that only a part of the oil on the inner periphery of the oil supply pump is guided to the inclined passage, and the characteristics are degraded as compared with the product of the present invention.

[0025]

According to the present invention, a high-efficiency compressor can be provided which can guide the oil supply capacity of an oil supply pump to an inclined passage with a small loss even if a rotary shaft having a relatively small diameter is used. be able to.

By providing a space in which no divider exists above the divider, the influence of the insertion angle of the divider and the relative angle of the inclined passage can be eliminated, and the assembly workability can be improved.

The substantially semi-lunar notch and press-fit portion of the divider can prevent unevenness in the amount of refueling due to uneven division between the divider and the inlet hole of the refueling pump, thereby improving workability and providing an inexpensive compressor. Become.

[Brief description of the drawings]

FIG. 1 is a sectional view of a hermetic electric compressor showing an embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part of the embodiment.

FIG. 3 is a sectional view taken along line III-III in FIG. 2;

FIG. 4 is a sectional view corresponding to FIG. 2, showing an operation state of the embodiment.

FIG. 5 is a schematic perspective view showing an operation state of the embodiment.

FIG. 6 is a perspective view of the divider according to the embodiment;

FIG. 7 is a characteristic diagram showing the number of rotations and the amount of oil in the embodiment and the conventional example.

FIG. 8 is a sectional view showing a conventional example 1.

FIG. 9 is a cross-sectional view showing a second conventional example.

FIG. 10 is a sectional view of a main part showing a conventional example 3;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 2 Closed container 3 Electric motor 4 Compression mechanism part 5 Block 7 Rotating shaft 9 Eccentric shaft 10 Connecting rod 12 Cylinder 13 Piston 17 Oil supply pump 18 Cylindrical bore 19 Slant passage 20 Spiral groove 21 Lower side hole

Claims (4)

[Claims] 1. A block provided with a compression mechanism in an airtight container, an electric motor disposed below the block,
The bearing of the block has a relatively small-diameter rotary shaft rotatably provided on the bearing, and an eccentric shaft with which a connecting rod operating a piston in a cylinder is engaged above the bearing of the rotary shaft. A refueling pump smaller in diameter than the rotating shaft is supported in a cylindrical bore formed at the lower end of the rotating shaft, the lower end of the cylindrical bore is open at the upper end so as to include the center, and the upper end reaches below the bearing. And, an inclined passage which is inclined outward from below and upward is provided, and further, a spiral groove is formed on an outer peripheral surface of the rotating shaft located on the bearing inner surface, and a lower end of the spiral groove is the inclined groove. A hermetic electric compressor that communicates with a lower horizontal passage that intersects with the passage and connects the upper end of the spiral groove directly with an eccentric passage provided on an eccentric shaft or with an upper horizontal passage. 2. A block having a compression mechanism in an airtight container, an electric motor disposed below the block,
The bearing of the block has a relatively small-diameter rotary shaft rotatably provided on the bearing, and an eccentric shaft with which a connecting rod operating a piston in a cylinder is engaged above the bearing of the rotary shaft. A refueling pump smaller in diameter than the rotating shaft is supported in a cylindrical bore formed at the lower end of the rotating shaft, the lower end is opened at the upper end of the cylindrical bore, and the upper end reaches below the bearing, and from below to above. An inclined passage which is inclined outwardly is provided, and a spiral groove is formed on the outer peripheral surface of the rotating shaft located on the inner surface of the bearing, and a lower end of the spiral groove has a lower side crossing the inclined passage. The upper end of the spiral groove is connected directly with the eccentric passage provided on the eccentric shaft or connected with the upper lateral passage,
A hermetic electric compressor in which a divider is inserted and locked in the refueling pump, and a space where no divider exists is provided between an upper end of the cylindrical bore and a lower end of the divider. 3. The divider has a vertically symmetrical shape, a substantially half-moon-shaped notch substantially at the center of the end, and a width near the center in the longitudinal direction that is slightly larger than that of the end. 3. The hermetic electric compressor according to claim 2, wherein the hermetic electric compressor is formed and fixed by press-fitting into an oil supply pump. 4. A block having a compression mechanism in an airtight container, an electric motor disposed below the block,
The bearing of the block has a relatively small-diameter rotary shaft rotatably provided on the bearing, and an eccentric shaft with which a connecting rod operating a piston in a cylinder is engaged above the bearing of the rotary shaft. A refueling pump smaller in diameter than the rotating shaft is supported in a cylindrical bore formed at the lower end of the rotating shaft, the lower end is opened at the upper end of the cylindrical bore, and the upper end reaches below the bearing, and from below to above. An inclined passage which is inclined outwardly is provided, and a spiral groove is formed on the outer peripheral surface of the rotating shaft located on the inner surface of the bearing, and a lower end of the spiral groove has a lower side crossing the inclined passage. The upper end of the spiral groove is connected directly with the eccentric passage provided on the eccentric shaft or connected with the upper lateral passage,
A divider is inserted and locked in the refueling pump, and a space where no divider exists is provided between the upper end of the cylindrical bore and the lower end of the divider. The divider has a vertically symmetrical shape, and a substantially half-moon is formed substantially at the center of the end. It has a notch, and the width near the center in the longitudinal direction is also slightly larger than the end to form a press-fit portion, which is press-fitted and fixed in the refueling pump, and has the diameter of the cylindrical bore and the inclined passage. A hermetic electric compressor in which the ratio of the diameters of 1: is set to 1: 0.6 to 0.8.