JPH0416639B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a rotary compressor that is incorporated into a refrigeration device such as a refrigerator or an air conditioner, and particularly relates to a rotary compressor that is installed in a refrigeration device such as a refrigerator or an air conditioner, and particularly relates to a rotary compressor that is installed in a refrigeration device such as a refrigerator or an air conditioner. The present invention relates to an oil supply system for a compressor.

[Background of the invention]

First, a conventional compressor will be explained.

FIG. 1 is a longitudinal sectional view showing an example of a conventional horizontal compressor. In the figure, reference numeral 1 denotes a case that also serves as an oil reservoir, and an electric motor 2 and a compression element 3 are housed within this case 1.

The electric motor 2 includes a stator 4 and a rotor 5, and a shaft 7 having a crank 6 and a shaft hole 8 formed in a hollow manner at one end is fitted into the rotor 5. .

The compression element 3 includes a cylinder 9 and a spring 1 inserted into a spring hole 10 bored in the cylinder 9.
1. The shaft 7, a bolt 14 that serves as the bearing of the shaft 7 and a side wall of the cylinder 9 and connects the side surface 12, the side plate 13, and the cylinder 9, which are arranged on both sides of the cylinder 9, and is fitted into the crank 6, A roller 15 that rotates eccentrically along the inside of the cylinder 9, a vane 16 that reciprocates within the groove 21 of the cylinder 9 with its tip abutting the roller 15 and the other end being pushed by the spring 11, and a back surface 17 of the vane 16. and the groove 21 of the cylinder 9 and the side plates 12,1
It consists of a pump chamber 18 surrounded by 3 and 3. The side plate 12 has a suction port 19 that can suck the lubricating oil 23 inside the case 1 into the pump chamber 18, and the side plate 13 has a discharge port 20 that can discharge the lubricating oil 23 from the pump chamber 18 into the oil supply path 21.
The oil supply passage 21 supplies lubricating oil to the shaft hole 8 at one end of the shaft, and can further supply lubricating oil from the shaft hole 8 through a branch hole 31 to required lubricating parts.

In this configuration, when the compressor is operated and the shaft 7 rotates, the roller 15 rotates accordingly, the vane 16 is pushed by the spring 11, and the vane 16 moves into the cylinder with its tip in contact with the roller 15. The refrigerant reciprocates in the groove 22 of No. 9, compresses the refrigerant that flows in from the refrigerant suction port (not shown), and discharges it from the refrigerant discharge port (not shown).

On the other hand, when the vane 16 reciprocates, the pump chamber 1
The volume of 8 changes and performs a pumping action. That is, when the volume of the pump chamber 18 increases, the lubricating oil 23 is sucked in from the suction port 19, and when the volume of the pump chamber 18 decreases, the lubricating oil 23 is sucked from the discharge port 20.
3 is discharged to the oil supply path 21. The lubricating oil sent to the oil feed path 21 is supplied to required lubricating parts through the shaft hole 8 and the branch hole 31.

However, when the suction port 19 and the discharge port 20 are provided separately on the side surfaces 12 and 13 on both sides, processing costs are required for machining the suction port 19 and the discharge port 20, respectively, which has the disadvantage of increasing costs. Ta.

In addition, in order to reduce this processing cost, side surfaces 12 and 1 are
The use of sintered alloys, which have higher material costs than cast metals, on both sides of 3 is also disadvantageous in terms of overall cost. Furthermore, in terms of reliability, if the suction port 19 is oriented downward so that the lubricating oil can be sucked in from the suction port 19 even if the oil level of the lubricating oil 23 drops to some extent, even if the material of the side surface 12 is Even when using a bonded metal, processing is complicated and costs are high.

In addition, in the example shown in Fig. 1, a horizontal compressor was described, but when a vertical compressor is applied, the suction port 19 is located above the cylinder 9, which has the disadvantage of making it difficult to secure a sufficient oil level for the lubricating oil 23. .

[Purpose of the invention]

The present invention eliminates the drawbacks of the prior art described above, and provides a compressor that can supply a sufficient amount of oil to the required lubricated parts even when the lubricating oil level is lowered, with low machining costs. Its purpose is to provide a refueling device.

[Structure of the invention]

In order to achieve the above object, the present invention includes, in a case that also serves as an oil reservoir, an electric motor, a cylinder, a shaft having a crank, a roller that is fitted in the crank and rotates eccentrically along the inside of the cylinder;
A vane that reciprocates in the groove of the cylinder while its tip is in contact with this roller, side plates provided on both sides of the cylinder, and a vane surrounded by the back surface of the vane, the groove of the cylinder, and the both side plates. a compression element having a pump chamber, a suction port and a discharge port communicating with the pump chamber, and the reciprocating movement of the vane as the shaft driven by the electric motor rotates, In a compressor configured to forcefully send lubricating oil flowing into a pump chamber from a discharge port through an oil supply path to a required lubrication part, the suction port and the discharge port are individually arranged on a side plate on one side of the cylinder. At the same time, the compressor oil supply system opened directly into the pump chamber.

[Embodiments of the invention]

The present invention will be explained below using examples.

FIG. 2 is a longitudinal sectional view of a compressor according to an embodiment of the present invention, FIG. 3 is a longitudinal sectional view showing details near the suction port and discharge port in FIG. 2, and FIG.
FIG. 4 is a sectional view taken along line A-A in FIG. 3; In the figure, parts given the same reference numerals as in FIG. 1 are the same parts.

The compressor of the embodiment shown in FIG. 2 includes, in a case 1, an electric motor 2, a cylinder 9 having a spring hole 10, a spring 11 inserted into the spring hole 10, a shaft 7 having a crank 6, and the crank 6. A roller 15 is fitted into the roller 15 and eccentrically rotates along the inside of the cylinder 9. A vane 16 moves reciprocally within the groove 22 of the cylinder 9 with its tip abutting the roller 15 and the other end being pushed by the spring 11. electric motor 2
A side plate 13A that is disposed on the opposite side of the cylinder 9 and has a space 25 and a discharge port 26 connected to the suction port 24 and the small diameter portion 24a of the suction port 24, and a side plate 12 that is disposed on the same side of the cylinder 9 as the electric motor 2.
A, an oil feed passage 21 that can supply the lubricating oil 23 discharged from the discharge port 26 to the shaft hole 8 of the shaft 7, a cover 28 provided with the oil feed passage 21, and a vane 1.
The compressor element 3A has a pump chamber 18A surrounded by a rear surface 17 of the pump 6 and side plates 12A and 13A. In the above compressor, the cross-sectional area of the small-diameter portion 24a of the suction port 24 is smaller than the cross-sectional area of the small-diameter portion 26a of the discharge port 26.

The operation of the compressor configured in this way will be explained.
When the compressor is operated and the shaft 7 rotates, the roller 15 rotates, and the vane 16 is pushed by the spring 11 and reciprocates within the groove 22 of the cylinder 9 while contacting the roller 15 with its tip. to compress the refrigerant.

On the other hand, when the volume inside the pump chamber 18A is about to increase due to the reciprocating movement of the vane 16, the lubricating oil 23 inside the case 1 is sucked through the suction port 24. At this time, lubricating oil is also sucked in from the discharge port 26, but the lubricating oil flows into the small diameter part 26a from a space 27 that is connected to the small diameter part 26a of the discharge port 26 and has a cross-sectional area larger than the cross-sectional area of this small diameter part 26a. Sometimes, a so-called edge effect occurs in which flow constricts at the small diameter portion 26a and large flow resistance occurs there, so that backflow is more difficult than in a case where a tapered discharge port 20 is provided. In this way,
Most of the lubricating oil is sucked in through the suction port 24.

When the vane 16 descends and the volume inside the pump chamber 18 becomes smaller, lubricating oil is discharged from the discharge port 26 to the oil feed path 21 side. At this time, lubricating oil is also discharged from the suction port 24 at the same time. In this case, if there is no space connected to the small diameter portion of the suction port 24 as shown in FIG. It flows like this, making it difficult for the edge effect to work. On the other hand, if the space 25 is provided as in the embodiment, as shown in FIGS. 3 and 4, the suction port small diameter portion 24a and the cylinder 9 will be partially heavy in the height direction. , since there is a distance between the two, the lubricating oil first expands in the space 25 and then reaches the small diameter portion 24.
Because the flow contracts at point a, the edge effect works, making it difficult for the flow to flow backwards.

In addition, since the cross-sectional area of the small-diameter portion 24a of the suction port 24 is made smaller than the cross-sectional area of the small-diameter portion 26a of the discharge port 26, the flow resistance from the pump chamber 18A to the shaft hole 8 of the shaft 7 is reduced. The resistance caused by the lubricating oil head becomes smaller than the backflow resistance from the pump chamber 18A to the case 1, and in conjunction with the effects of the spaces 25 and 27, most of the lubricating oil discharged from the pump chamber 18A flows through the oil feed path 21. The required lubricating parts are supplied with oil.

In addition, as shown by the streamlines in FIG. 6, which is an enlarged view of FIG.
a, and a large diameter portion 2 of the discharge port with a smooth roundness.
6b in the space 25, when lubricating oil is discharged from the pump chamber 18A, the edge effect of the small diameter portion of the suction port 24a makes it more difficult for the lubricating oil to flow back, and the oil flows to the discharge port 26 where the flow resistance is lower. It becomes easier.

Next, the effect of the space 25 on changes in the kinematic viscosity of lubricating oil will be explained using FIG. 7. In FIG. 7, 29 indicates the fifth position near the pump chamber 18A.
If space 25 is not provided as shown in the figure, 3
0 indicates the amount of oil to be supplied when a space 25 is provided as shown in FIG. 3 of this embodiment. As is clear from FIG. 7, in the case where the space 25 is provided, the amount of oil supplied changes continuously in response to changes in the kinematic viscosity of the lubricating oil. On the other hand, in the case where there is no space 25, when the kinematic viscosity increases, the amount of oil supplied decreases rapidly midway, and at higher kinematic viscosity, the amount of oil supplied becomes almost zero. This is because as the kinematic viscosity increases, the overall flow resistance up to the shaft 9 increases, and in the case where the space 25 is not provided, there is a lot of backflow from the suction port 24, and the lubricant does not rise to the height of the shaft 9. , whereas space 2
This is because the one provided with 5 has a large edge effect and can supply oil up to a higher kinematic viscosity.

Other performance effects of this example include:
By covering the suction port 24 with the cover 28,
It is possible to supply the lubricating oil 23 until the level of the lubricating oil 23 drops to near the lower end of the cover 28, thereby increasing reliability.

A major cost advantage of this embodiment is that the suction port 24 and the discharge port 26 are located on the same side plate 13.
A and opening directly into the pump chamber 18A, it is only necessary to process the suction port 24 and the discharge port 26 on the side surface 13A.
Compared to machining the discharge port 20, it can be manufactured at a lower cost. In addition, one side plate 13A
By providing both ports together, side plate 1
Only for 3A, the material cost is a little expensive, but by using a sintered alloy that is easy to achieve dimensional accuracy, these ports can be formed at the same time during sintering.
This is a major cost advantage.

In the embodiment shown in FIG. 3, a horizontal compressor in which the shaft 7 is horizontal is shown, but the shaft 7 is horizontal.
As shown in the figure, when applied to a vertical compressor in which the shaft 7 is approximately vertical, the first Compared to the case where the suction port 19 is provided on the electric motor 2 side as shown in the figure, there is an advantage that the tolerance range for the drop in the oil level of the lubricating oil 23 is widened.

Further, in the vertical compressor shown in FIG. 8, the spring hole 10 is closed with a hole seal 32. This is because in the horizontal compressor shown in the above embodiment, the spring hole 10 is located below the oil level and the gap between the cylinder 9 and the case 1 is filled with oil, so that the spring hole 10 is not sealed. However, when the spring hole 10 is above the oil level as in this embodiment, gas leaks between the cylinder 9 and the case 1 and the spring hole 10 cannot be completely sealed, causing gas to enter the pump chamber 18A. This is because leakage may occur and the performance of the oil supply pump may be impaired. However, the hole seal 32
By blocking the spring hole 10 with the above, a larger amount of oil can be supplied.

In addition, in the embodiment shown in FIG.
The diameter of the oil supply port 34 provided in the shaft hole 8 is made smaller than the diameter of the shaft hole 8. This is because the lubricating oil supplied to the shaft hole 8 obtains centrifugal force due to the rotation of the shaft 7 and flows out of the shaft hole 8. Therefore, if the oil filler port 34 is large, the momentum of the oil flowing out is increased. Fuel filler port 34
This creates resistance to the flow of oil flowing in, reducing the performance of the oil supply pump. However, since the diameter of the oil filler port 34 is made smaller than the diameter of the shaft hole 8,
The momentum of the oil flowing back due to centrifugal force can be further reduced, which improves the performance of the oil supply pump.

Furthermore, the oil supply device for the vertical compressor described above has the following advantages. This will be explained using FIG. 9. 35 shows the relationship between the amount of oil supplied to the compressor rotation speed in the case of the vertical compressor according to this embodiment, and 36 in the case of the centrifugal oil supply pump used in many conventional vertical compressors. Conventional centrifugal oil pumps have a structure in which oil is transmitted up the inner wall surface of the shaft hole 8 by centrifugal force as the shaft 7 rotates, but when used in a compressor that controls the rotation speed. Since the centrifugal force is proportional to the square of the rotation speed, the amount of oil supplied also forms a quadratic curve as shown in FIG. Therefore, for example, an oil supply pump that can provide an appropriate amount of oil at a compressor rotation speed of approximately 3600 rpm has the disadvantage that the amount of oil supply is insufficient at low speed rotation, and too much at high speed rotation.
However, since this example is a positive displacement oil supply pump, the amount of oil supplied is almost proportional to the number of rotations, so there is no significant drop in the amount of oil supplied even at low speeds, and there is no sudden increase even at high speeds. Therefore, an appropriate amount of oil supply can be obtained over a wide range of operating speeds.

〔Effect of the invention〕

In the present invention, the suction port and the discharge port are individually arranged on the side plate on one side of the cylinder and open directly into the pump chamber, so that processing costs can be reduced and each port has a forward flow path. Since the resistance can be made smaller than the flow path resistance in the reverse direction and the forward flow rate can be made larger than the reverse flow rate, it is possible to provide a compressor oil supply device that can supply sufficient lubricating oil to required lubricating parts.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing an example of a conventional compressor, FIG. 2 is a longitudinal sectional view showing a compressor according to an embodiment of the present invention, and FIG. 4 is an enlarged view of the vicinity of the discharge port, FIG. 4 is a cross-sectional view taken along line A-A in FIG. 3, FIG. The longitudinal sectional view corresponding to the figure, Fig. 7, is
It is a kinematic viscosity of lubricating oil - oil supply amount diagram. Figure 8 shows
FIG. 9 is a vertical sectional view showing an embodiment of the present invention applied to a vertical compressor, and is a rotation speed-oil supply amount diagram showing the effect of the oil supply device for the vertical compressor in FIG. 8. DESCRIPTION OF SYMBOLS 1... Case, 2... Electric motor, 3... Compression element, 6... Crank, 7... Shaft, 9... Cylinder, 12A... Side plate, 13A... Side plate, 15
...Roller, 16... Vane, 17... Vane back, 18A... Pump chamber, 21... Oil feed path, 22
... Groove, 23 ... Lubricating oil, 24 ... Suction port,
24a...Suction port small diameter part, 25...Space, 26...Discharge port, 28...Cover, 32
... Hole seal, 33 ... Oil supply path, 34 ... Oil supply port.

Claims (1)

[Scope of Claims] 1. A case that also serves as an oil reservoir contains an electric motor, a cylinder, a shaft having a crank, a roller that is fitted into the crank and rotates eccentrically along the inside of the cylinder, and a tip of which touches the roller. a vane that reciprocates within the groove of the cylinder while contacting the cylinder;
The compression element includes side plates disposed on both sides of the cylinder, a pump chamber surrounded by the back surface of the vane, a groove of the cylinder, and the side plates, and a suction port and a discharge port communicating with the pump chamber. Due to the reciprocating movement of the vane as the shaft driven by the electric motor rotates, the lubricating oil that has flowed into the pump chamber through the suction port is transferred from the discharge port to the required lubrication section through the oil supply path. An oil supply device for a compressor configured to perform pressure feeding, wherein the suction port and the discharge port are individually arranged on a side plate on one side of the cylinder and open directly into the pump chamber. . 2. The compressor oil supply device according to claim 1, wherein at least one of the suction port and the discharge port is a fluid diode. 3. The oil supply device for a compressor according to claim 1, wherein the material of the side plate provided with the suction port and the discharge port is a sintered alloy.