JPH0799153B2 - Refueling device for horizontal compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an oil supply device for a horizontal compressor, and, for example, a horizontal compressor incorporated in a refrigeration device such as a refrigerator or an air conditioner is provided with a required lubrication section. The present invention relates to an oil supply device for a horizontal compressor suitable for appropriately supplying lubricating oil.

[Conventional technology]

A conventional horizontal compressor oil supply device is, for example, a full-scale model 55-60.
As described in Japanese Patent No. 489, a suction port that guides the lubricating oil in the closed container to the pressure fluctuation chamber and a pressure feed pipe that feeds oil from the pressure fluctuation chamber to the axis of the horizontal rotary shaft are respectively one pipe. Was becoming.

However, when the sliding vanes reciprocate to increase the volume of the pressure fluctuation chamber, the lubricating oil is sucked from the suction port, but at the same time, the lubricating oil also flows back into the pressure fluctuation chamber from the pressure feed pipe side. Further, when the volume of the pressure fluctuation chamber becomes small, the lubricating oil is discharged from the pressure feeding pipe side, but at the same time, the lubricating oil is discharged into the closed container from the suction port as well, so that the lubricating oil also flows backward.

Especially, in the discharge stroke of the fuel pump,
Since a line resistance from the pressure feed pipe to the tip of the axis of the horizontal rotary shaft and a lubricating oil head up to the height of the axis are required, the resistance on the pressure feed pipe side is large, and the lubricating oil flows to the suction port side. Backflow is easy, and the amount of lubricating oil sent to the axis of the horizontal rotary shaft is small. Especially when the rotational speed of the compressor is reduced, the lubricating oil does not reach the height of the horizontal rotary shaft. It was not considered enough.

[Problems to be Solved by the Invention]

Further, as prior art developed by the present inventors, for example,
A horizontal compressor described in JP-A-59-226293 is known.

In this publication, the suction port has a small diameter portion on the side that opens to the pump chamber side, the side that opens inside the case has a large diameter portion, and the discharge port has a small diameter portion that opens on the oil supply path side. The side that opens to the side is a large diameter portion, and the flow path area ratio of the large diameter portion and the small diameter portion of at least one of the suction port and the discharge port, that is, the (large diameter portion area / small diameter portion area) value A value of 4.0 or more is disclosed.

However, this prior art merely sets the shape of the fluid diode (large-diameter portion cross-sectional area / small-diameter portion cross-sectional area) that can ensure the performance of the fuel pump.

The present invention has been made to solve the above-mentioned problems of the prior art, and a first object of the present invention is to secure a flow rate of an oil supply pump at a low speed and a discharge head, and to supply lubricating oil to a required lubricating portion. An object of the present invention is to provide an oil supply device for a horizontal compressor that can be appropriately supplied.

Further, in the oil pump targeted by the present invention, when the cross-sectional area of the small diameter portion of the fluid diode is small, or in the region where the rotation speed is large as a result of the rotation speed control, the resistance of the suction port, the discharge port, etc. The pressure fluctuation amplitude may become large, and the refrigerant gas dissolved in the lubricating oil may appear as bubbles. If this lubricating oil mixed with bubbles is supplied as it is to the bearing or the like, the allowable bearing load will decrease due to the compression action of the bubbles.

A second object of the present invention is to provide an oil supply device for a horizontal compressor capable of reducing pressure fluctuations in the oil supply pump, suppressing the generation of bubbles in the lubricating oil, and reducing the power of the oil supply pump.

[Means for Solving the Problems]

In order to achieve the above-mentioned first object, a first aspect of the invention relates to an oil supply device for a horizontal compressor of the present invention. A compression mechanism portion is housed, and the compression mechanism portion includes a cylinder, a roller fitted to a crank of the rotary shaft and eccentrically rotated along the inside of the cylinder, and a groove of the cylinder while abutting the roller. A reciprocating vane and a side plate that also serves as a bearing for the rotating shaft and a side wall of the cylinder are provided with a suction port and a discharge port for lubricating oil, and the rear face of the vane and the groove of the cylinder are provided. A pump chamber for refueling surrounded by and the side plate, and by the pumping action by the reciprocating motion of the vane accompanying the rotation of the rotary shaft, from the bottom of the hermetic container through the suction port, The lubricating oil that has flowed into the pump chamber is pressurized, and the lubricating oil is pressure-fed from the pressurizing / discharging port to the oil supply section of the rotary shaft via an oil feeding passage, and the suction port is opened to the pump chamber. Is a small diameter part and the side that opens to the bottom of the closed container is a large diameter part, and the discharge port is a small diameter part that opens to the oil supply passage and the large diameter part that opens to the pump chamber. In a lubrication device for a horizontal compressor having a tapered port, a cross-sectional area of a small diameter portion of the suction port is A (m ² ), a compressor rotation speed is N (rps), and a volume change amount per rotation of the oil supply pump is V (V). The cross-sectional area of the small diameter part of the suction port is set so that N · V / A> 1.0 when (m ³ ).

In order to achieve the above-mentioned second object, a second invention relating to the oil supply device for a horizontal compressor of the present invention is the same as the above-mentioned first invention, in the upper part of the oil feed passage, there is a space inside the hermetic container. It is provided with an opening for opening.

[Action]

 The way of thinking and the function of the above technical means were described.

When the compressor rotates at low speed, in order to supply the lubricating oil stored in the bottom of the closed container to the height of the shaft, the discharge port, the line resistance of the oil passage and the suction port that only overcomes the head up to the shaft height. Resistance is required, which requires a high flow rate at the suction port. The required flow velocity can be determined by the displacement volume of the pump and the cross-sectional area of the suction port.

Therefore, in the first aspect of the present invention, the cross-sectional area of the suction port is set to a specific value so that the reverse flow rate from the suction port can be reduced and the required amount of oil supply can be obtained even at low speed rotation.

Further, in the second invention, an opening is provided in the upper part of the oil supply passage,
Excess lubricating oil is separated during high-speed rotation, and only the necessary amount of oil is supplied to the oil supply port of the rotating shaft (hereinafter referred to as the shaft). That is, when the rotation speed of the compressor is high, the amount of lubricating oil supplied by the pump increases, and the amount of oil flowing from the oil supply passage to the shaft center of the shaft also increases, which increases the resistance generated here. Extra oil and power are generated. Therefore, in the second aspect of the invention, by opening the upper part of the oil feed passage and allowing an excess amount of oil to escape, a necessary amount is supplied to the lubrication portion, the (flow) resistance at the shaft center is reduced, and excess power is supplied. I tried to omit it.

Further, when the pressure fluctuation amplitude in the pump chamber becomes large due to the resistance of the suction port and the discharge port at high speed rotation, the refrigerant dissolved in the lubricating oil may melt and fine bubbles may appear in the lubricating oil. is there.

If this lubricating oil mixed with bubbles is supplied as it is to the bearing or the like, the allowable bearing load will be reduced due to the compression action of the bubbles. In the second aspect of the present invention, by providing the opening in the upper part of the oil feed passage, it is possible to reduce the pressure fluctuation in the pump chamber and suppress the generation of bubbles in the lubricating oil.

〔Example〕

Embodiments of the present invention will be described below with reference to FIGS. 1 to 10.

First, FIG. 1 is a vertical cross-sectional view of a horizontal rotary compressor according to an embodiment of the present invention, and FIG. 2 is a detailed cross-sectional view around a pump chamber of an oil supply device in FIG.

As shown in FIG. 1, the horizontal rotary compressor according to the present embodiment has a compression mechanism portion in which a motor 1 is directly connected to a case 1 of a hermetically sealed container and a shaft 4 of a rotary shaft is connected to the motor 21.
22 are stored, and lubricating oil 13 is stored at the bottom.

The lubricating oil is preferably an oil in which a fluorine-based refrigerant is dissolved.

The electric motor 21 is composed of a stator 19 fixed to the case 1 and a rotor 20 fitted to the shaft 4.

The compression mechanism portion 22 includes a cylinder 2 and a roller 7 which is fitted to the crank 3 provided on the shaft 4 and eccentrically rotates along the inside of the cylinder 2, and inside the groove 8 of the cylinder 2 while contacting the roller 7. The main components are a vane 10 that reciprocates to compress the refrigerant gas, side plates 5 and 6 that serve as side walls that seal the bearing of the shaft 4 and both sides of the cylinder 2, and a refrigerant gas suction port and a discharge port (not shown). As an element.

Reference numeral 16 indicates that the compressed discharge gas is the stator 19 and the rotor.
It shows a gas flow path leading to a discharge pipe (not shown) through 20.

As an oil supply device in the compression mechanism portion 22, the side plate 5 is provided with a lubricating oil suction port 26, the side plate 6 is provided with a lubricating oil discharge port 28, and the rear face 11 of the vane 10 and the groove 8 of the cylinder 2 are provided. The pump chamber 12 for refueling is surrounded by the side plates 5 and 6, the spring hole 23, and the seal part 24 provided at the lower end thereof. The side plate cover 25 fixed to the side surface of the side plate 6 is provided with a lubricating oil supply port 33, which communicates with the discharge port 28 to the shaft hole 17 of the shaft 4, and the upper part thereof is provided in the inner space of the case 1. An oil feed passage 32 having an opening 40 that opens is connected.

The shaft 4 is provided with a branch hole 18 that communicates the shaft hole 17 with each lubricating portion of the compression mechanism portion 22.

The suction port 26 and the discharge port 28 will be described in more detail with reference to FIG.

The suction port 26 provided in the side plate 5 has a suction piece 38 having a tapered flow path 36 in which the side opening to the pump chamber 12 is a small diameter edge portion 34 and the side opening to the bottom of the case 1 is a large diameter portion. It is attached to the side plate 5, and depending on the flow direction of the fluid, the edge portion 34 serves as a resistance portion and the fluid flows to one side and does not flow to the other. It has a so-called fluid diode structure.

A space 27 is formed at the outlet of the suction port 26 with the fluid diode, and a communication passage 30 that connects the space 27 and the pump chamber 12 is formed in the side plate 5.

On the other hand, the discharge port 28 provided in the side plate 6 has a tapered flow path 37 in which the side opening to the oil feed passage 32 is the edge portion 35 of the small diameter portion and the side opening to the pump chamber 12 is the large diameter portion. ,
It has a so-called fluid diode structure.

A space 29 is formed at the outlet of the discharge port 28 with the fluid diode, and a communication passage 31 that connects the space 29 and the oil feed passage 32 is formed in the side plate 6.

The inner diameter φ _ds of the edge portion 34 is called the suction port diameter, and the inner diameter φ _dD of the edge portion 35 is called the discharge port diameter.

The operation of the horizontal rotary compressor thus configured will be described.

When the compressor is operated and the shaft 4 rotates, the roller 7 rotates accordingly, and the vane 10 is reciprocated in the groove 8 of the cylinder 2 while being pressed by the spring 9 and abutting the tip of the roller 7. . Then, the cylinder 2, the roller 7, and the vane
The refrigerant is compressed by the volume change of the portion surrounded by 10.

Next, the operation of the oil supply pump according to the oil supply device for the horizontal rotary type compressor of the present embodiment will be described.

When the volume of the refueling pump chamber 12 is about to increase due to the reciprocating motion of the vane 10, the suction port 26 causes the case 1
The lubricating oil 13 inside is sucked. At this time, the lubricating oil 13 is also sucked from the discharge port 28 at the same time, but the flow of the lubricating oil expanded in the space 29 connected to the discharge port 28 is contracted at the tip of the discharge port 28, and there A large flow resistance is generated, which makes it difficult to backflow. Therefore, most of the lubricating oil is sucked through the suction port 26.

On the other hand, when the vane 10 descends and the volume in the pump chamber 12 becomes small, the lubricating oil is discharged from the discharge port 28 to the oil feed passage 32 side. At this time, the lubricating oil is also discharged from the suction port 26 at the same time, but the flow of the lubricating oil expanded in the space 27 provided by connecting to the suction port 26 contracts at the tip of the suction passage port 26, and a large flow occurs there. Since it causes resistance, it is difficult to backflow. Therefore, most of the lubricating oil is discharged from the discharge port 28, passes through the communication portion 31, the oil feed passage 32, and the side plate cover 25.
The lubricating oil is lifted up to the height of the lubricating oil supply port 33 provided in the. From the lubricating oil supply port 33 to the shaft 4
Lubricating oil flows into the shaft hole 17 and the required amount of lubricating oil can be supplied to the required lubrication portion through the branch hole 18. When the amount of oil flowing into the shaft hole 17 is large and the shaft hole 17 is filled, the excess oil amount out of the amount of oil sent from the oil feed passage 32 is discharged from the opening 40 provided at the upper portion of the oil feed passage 32. You can do it.

By the way, the head of the lubricating oil lifted by the oil supply pump of this embodiment is mainly determined by the resistance of the suction port 26.

The resistance of the suction port 26 is proportional to the square of the flow velocity at the suction port 26. Therefore, when the rotation speed of the compressor becomes low and the flow rate pushed out from the pump chamber 12 becomes small, the flow velocity at the suction port 26 becomes small and the resistance becomes small. As a result, the head on the discharge side becomes smaller, and the lubricating oil cannot be lifted to the height up to the lubricating oil supply port 33. Therefore, in order to obtain a sufficient ejection head at a desired low rotation speed, it is necessary to reduce the cross-sectional area of the suction port 26 and increase the flow velocity.

The relationship between the rotational speed N (rps) and the required cross-sectional area A (m ² ) of the small diameter portion of the suction port 26 should be expressed using the volume change amount V (m ³ ) of the pump chamber 12 per one rotation. You can The volume change amount V (m ³ ) is the difference in volume between the top dead center and the bottom dead center of the vane 10.

Here, an example of the flow rate characteristic with respect to the rotation speed of the oil supply pump 12 will be described with reference to FIG.

FIG. 3 is a diagram showing the relationship between the number of revolutions of the oil supply pump of FIG. 2 and the pump flow rate, where the horizontal axis shows the number of revolutions N and the vertical axis shows the pump flow rate Q.

As is clear from FIG. 3, the pump flow rate Q is the number of revolutions N
Becomes lower at a constant rate and becomes zero at a certain rotation speed. When this rotation speed is set to the minimum rotation speed N _min , this minimum rotation speed N _min is a limit at which the head up to the lubricating oil supply port 33 can be maintained.

This minimum rotation speed N _min is reduced by decreasing the cross-sectional area of the small diameter portion of the suction port 26, that is, the suction port cross-sectional area A (m ² ) and increasing the flow velocity at the edge portion 34 of the suction port 26 (hereinafter referred to as the port flow velocity). can do.

Next, FIG. 4 is a diagram showing the relationship between the flow rate relation value of the oil supply pump of FIG. 2 and the volumetric efficiency with respect to the displacement volume of the pump, and the horizontal axis relates to the port flow velocity of the suction port 26. As the value, α = V · N / A (m / s) is taken, and the vertical axis shows the volume efficiency Q / Q ₀ for the displacement volume Q ₀ of the pump. Here, Q is the pump flow rate as described above, Q ₀ is the displacement volume per unit time, and the relationship between V and Q ₀ is V · N
= Q ₀ . α indicates the flow rate of oil.

In the figure, A ₀ (m ² ) is the taper flow path 36 of the suction port 26.
3 is a diagram showing the cross-sectional area of the large-diameter portion of and the diagram is shown with the ratio A / A ₀ with the cross-sectional area A (m ² ) of the small-diameter portion as a parameter.

As is clear from FIG. 4, if α> 1.0, the lubricating oil can be supplied. That is, the desired low speed N
(Rps), the small diameter part of suction port 26 (edge part 3
4) If the cross-sectional area A (m ² ) is set so small that α = V · N / A> 1.0, it can function as an oil pump.

Here, if V · N / A> 1.0 in the above equation is transformed, N>
It can be seen that A / V, and the ratio of A and V must be smaller than the rotational speed.

In other words, the volume change N _min · of the pump chamber per unit time (1 sec) during operation of the minimum rotation speed (N _min ) of the compressor
Desirable by setting the cross-sectional area A of the small diameter portion of the suction port 26 so that the ratio of V (m ³ / s) and the cross-sectional area A (m ² ) of the small diameter portion of the suction port 26 exceeds 1.0. It is possible to properly maintain the supply of the lubricating oil when the compressor rotates at a low speed.

Next, the effect of providing the opening 40 in the upper part of the oil feed passage 32 will be described.

As the number of revolutions of the compressor increases, the amount pushed out and the amount sucked by the vane 10 increase in proportion to the number of revolutions.

Therefore, the suction port 26, the discharge port 28 and the oil passage
The amount of lubricating oil flowing through 32 increases, which increases resistance.

A conventional compressor without an opening (for example, Japanese Patent Laid-Open No.
In JP-A-59-226293), the lubricating oil is filled in the shaft hole 17 of the shaft 4, and the reciprocating motion of the vane 10 is accompanied by the oil feeding passage.
A large amount of lubricating oil flows from 32 to the shaft hole 17. This causes a large flow resistance, and as a result, the pressure fluctuation amplitude in the pump chamber 12 becomes large, and a large amount of power is required for the amount of lubricating oil required to be supplied to the lubricating portion from the shaft hole 17 through the branch hole 18. It was supposed to be consumed.

However, in the present embodiment, the opening 40 is provided above the oil supply passage 32 at a position higher than the lubricating oil supply port 33, and the pump chamber 12
The lubricating oil that has been lifted up to the height of the lubricating oil supply port 33 through the discharge port 28 and the oil feed passage 32 flows from the lubricating oil supply port 33 into the shaft hole 17 of the shaft 4. Then, the required amount of lubricating oil is supplied to each lubricating portion through the branch hole 18 by the centrifugal force generated by the rotation of the shaft 4. Then, the excess lubricating oil that does not flow into the shaft hole 17 will not be released.
It is discharged from 40 to the space inside Case 1.

As described above, by providing the opening 40, the oil in the shaft hole 17 has a small flow and a small resistance. Further, since the opening 40 is provided, the resistance for closing the discharge side is reduced. By combining these effects, the resistance on the discharge side can be reduced, so that the pressure fluctuation amplitude in the pump chamber 12 can be reduced. Therefore, the power of the oil supply pump can be reduced.

When a lubricating oil in which a fluorine-based refrigerant is dissolved is used as the lubricating oil for the horizontal rotary compressor of this embodiment, the lubricating oil is saturated with the fluorine-based refrigerant in a steady operation state. When the lubricating oil in such a state is sucked into the pump chamber 12, the pressure fluctuation amplitude of the pump chamber 12 increases as the rotation speed increases, and the pump chamber 12 becomes a negative pressure during the suction stroke of the pump. The refrigerant in the oil melts out to form fine bubbles that are mixed in the lubricating oil.

However, since the opening 40 is provided above the oil supply passage 32,
It is possible to reduce the pressure fluctuation in the pump chamber 12, suppress the generation of bubbles in the lubricating oil, and reduce the extra pump power generated at high speed.

Next, another embodiment in which an opening is provided in the upper part of the oil feeding passage
This will be described with reference to the drawings and FIG.

FIG. 5 is a partial cross-sectional view showing an oil supply device for a horizontal rotary type compressor according to another embodiment of the present invention, and FIG. 6 is a partial top view of FIG. In the figure, those having the same reference numerals as those in FIGS. 1 and 2 are the same parts as those in the previous embodiment, and therefore their explanations are omitted.

The oil passage 32A in FIGS. 5 and 6 is fixed to the side plate cover 25 and is composed of a U-shaped pipe that connects the space 29 at the outlet of the discharge port 28 and the lubricating oil supply port 33A at one end of the shaft 4. There is. Then, at the upper part of this oil supply passage 32A, the opening 4
0A is drilled.

According to the embodiment shown in FIGS. 5 and 6, exactly the same effect as that of the embodiment shown in FIGS. 1 and 2 is expected, and the pressure is released so that the flow resistance of the lubricating oil in the shaft hole 17 is omitted. By doing so, it is possible to reduce the resistance on the discharge side, reduce the pressure fluctuation amplitude in the pump chamber 12, and reduce the power of the pump.

Further, there is an advantage that even if the amount of oil sent from the oil feed passage 32A decreases at low speed, the lubricating oil can be poured from the lubricating oil feed hole 33A into the shaft hole 17 with little resistance.

Next, still another embodiment in which an opening is provided in the upper portion of the oil feeding passage will be described with reference to FIGS. 7 and 8.

FIG. 7 is a partial cross-sectional view showing an oil supply device for a horizontal rotary compressor according to still another embodiment of the present invention, and FIG.
FIG. 8 is a partial side view taken along the arrow B of FIG. 7. In the figure, the same reference numerals as those in FIGS. 1 and 2 are the same parts, and thus the description thereof will be omitted.

The oil passage 32B in FIGS. 7 and 8 is provided so that one end communicates with the space 29 at the outlet of the discharge port 28 in the side plate cover 25, and the other end is opened as an opening 40B. Then, an oil guide 41 having an open upper portion is provided so as to receive the oil discharged from the opening 40B and fixed to the side plate cover 25, and the shaft 4 is passed through the lubricating oil supply port 33B formed in the side plate cover 25.
It is configured to communicate with the shaft hole 17 of.

Lubricating oil sent through the oil feed passage 32B is discharged from the opening 40B, poured into the shaft hole 17 of the shaft 4 from the lubricating oil supply port 33B by the oil guide 41, and slides through the branch hole 18. Supply the required amount of lubricating oil to the parts. Then, excess lubricating oil during high-speed operation is discharged from the upper part of the oil guide 41 into the internal space of the case 1 and returned to the oil sump at the bottom of the case 1.

According to the embodiment shown in FIGS. 7 and 8, the same effect as that of the embodiment shown in FIGS. 1 and 2 can be expected. The flow resistance in the shaft hole 17 is omitted, and the oil feed passage is provided by the opening 40B. By releasing the pressure in 32B, the resistance on the discharge side can be reduced, the amplitude of pressure fluctuation in the pump chamber 12 can be reduced, and the power of the pump can be reduced.

Further, in the present embodiment, one end of the oil supply passage 32B is directly opened to the opening 40B.
Therefore, there is an advantage that the resistance is further smaller than that of the opening having the branch portion.

In each of the above embodiments, one side plate 5 is provided with a suction port 26 with a fluid diode, and the other side plate 6 is provided with a discharge port 28 with a fluid diode. The suction port 26 and the discharge port 28 may be provided on the side plate, for example, the side plate 5. In each of the above-described embodiments, the lubricating oil is supplied from the discharge port 28 to the shaft hole 17 of the shaft 4 through the oil feed passage 32, but it may be supplied directly to the surface of the shaft 4. An example will be described below.

FIG. 9 is a vertical cross-sectional view of a horizontal rotary compressor according to still another embodiment of the present invention, and FIG. 10 is a partially enlarged cross-sectional view showing details of the oil supply device in FIG. In the figure, the first and second
The same reference numerals as those in the figure are the same parts and perform the same operation, and therefore the description thereof will be omitted.

In the embodiment of FIGS. 9 and 10, one side plate 50 is provided with a suction port 26A with a fluid diode and a discharge port 28A with a fluid diode, and the other side plate 6A is not provided with an oil feed passage. It was done like this.

The side plate 50 has a space 27A formed at the outlet of the suction port 26A and a space 29A formed at the outlet of the discharge port 28A. The space 27A communicates with the pump chamber 12 and the space 29A communicates with the oil supply passage 51. ing.

The suction port 26A and the discharge port 28A respectively include a suction piece 38 and a discharge piece 39 having tapered flow paths.

Similarly, in the side plate 50, an oil feed passage 51 is bored so that the shaft oil passage 52 provided on the surface of the shaft 4 and the space 29A are communicated with each other. An opening 53 is provided to communicate with the space.

Reference numeral 15 denotes an oil groove for lubricating oil provided on the surface of the shaft 4.

The horizontal rotary compressor configured in this way is also the first
The same operation as that of the embodiment shown in FIG. 2 is performed and the same effect is obtained.

That is, even if the rotation speed of the compressor is low, it is possible to supply a sufficient amount of oil supply, and when the rotation speed of the compressor is high, supply the required amount of lubricating oil to the lubricating oil and Since the resistance can be reduced, there is an effect of reducing extra power of the pump.

Also, only one side plate 50 has suction port 26A and discharge port 2
Since 8A is provided and the oil supply path 51, the opening 53, etc. are drilled in the same part, the number of parts and processing man-hours of the compressor are more than those of the compressor shown in FIGS. 1 and 2 above. There is an advantage of reducing.

〔The invention's effect〕

As described in detail above, according to the present invention, it is possible to provide an oil supply device for a horizontal compressor capable of ensuring an oil supply pump flow rate and a discharge head at a low speed and appropriately supplying lubricating oil to a required lubrication portion. You can

Further, according to the present invention, it is possible to provide an oil supply device for a horizontal compressor capable of reducing the pressure fluctuation in the oil supply pump, suppressing the generation of bubbles in the lubricating oil, and reducing the power of the oil supply pump.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a horizontal rotary compressor according to an embodiment of the present invention, FIG. 2 is a detailed cross-sectional view around a pump chamber of an oil supply device in FIG. 1, and FIG. FIG. 4 is a diagram showing the relationship between the number of revolutions of the oil supply pump and the pump flow rate, and FIG. 4 is a diagram showing the relationship between the flow velocity relationship value of the oil supply pump of FIG. 2 and the volume efficiency with respect to the displacement volume of the pump, FIG. 5 is a partial cross-sectional view showing an oil supply device for a horizontal rotary type compressor according to another embodiment of the present invention, FIG. 6 is a partial top view taken along arrow A of FIG. 5, and FIG. A partial cross-sectional view showing an oil supply device for a horizontal rotary type compressor according to still another embodiment of the present invention,
FIG. 8 is a partial side view as seen from the arrow B of FIG. 7, FIG. 9 is a vertical sectional view of a horizontal rotary compressor according to still another embodiment of the present invention, and FIG. It is a partial expanded sectional view which shows the detail of an oil supply apparatus. 1 ... Case, 2 ... Cylinder, 3 ... Crank, 4 ...
… Shaft, 5,6,6A …… Side plate, 7 …… Roller, 8 ……
Groove, 9 ... Spring, 10 ... Vane, 11 ... Rear surface, 12 ... Pump chamber, 13 ... Lubricating oil, 15 ... Oil groove, 17 ... Bearing, 18 ...
… Branch hole, 19 …… stator, 20 …… rotor, 21 …… motor, 22 …… compression mechanism, 25 …… side plate cover, 26,26A ……
Suction port, 28,28A …… Discharge port, 27,27A, 29,29A…
… Space, 32,32A, 32B …… Oil supply passage, 33,33A, 33B …… Lubricating oil supply port, 35,35 …… Edge part, 36,37 …… Tapered passage, 38 …… Suction piece, 39 ...... Discharge piece, 40, 40A, 40B
...... Opening port, 41 ...... Oil guide, 50 ...... Side plate, 51 ...... Oil passage, 52 ...... Shaft oil passage, 53 ...... Opening port.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroshi Iwata 292 Yoshida-cho, Totsuka-ku, Yokohama, Kanagawa Prefecture Home Appliances Research Laboratory, Hitachi, Ltd. Hitachi Co., Ltd. Tochigi Plant (72) Inventor Masahiko Sugiyama 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture Hitachi Co., Ltd. Tochigi Plant (56) Reference JP-A-59-226293 (JP, A)

Claims (3)

[Claims] 1. An electric motor and a compression mechanism portion directly connected to the electric motor via a rotary shaft are housed in a closed container having a bottom portion containing lubricating oil, and the compression mechanism portion includes a cylinder and a crank of the rotary shaft. A roller which is fitted and rotates eccentrically along the inside of the cylinder, a vane which reciprocates in the groove of the cylinder while contacting the roller, and a side plate which also serves as a bearing for the rotary shaft and a side wall of the cylinder. The side plate is provided with a suction port and a discharge port for lubricating oil, and is provided with a pump chamber for oil supply surrounded by the back surface of the vane, the groove of the cylinder and the side plate. The pumping action of the reciprocating motion of the vanes pressurizes the lubricating oil that has flowed into the pump chamber from the bottom of the closed container via the suction port, and then pressurizes the lubricating oil from the discharge port through an oil feed passage. The suction port is configured to be pressure-fed to the oil supply portion, and the suction port is a tapered port having a small diameter portion on the side opening to the pump chamber and a large diameter portion on the side opening to the closed container bottom, and In a lubrication device for a horizontal compressor, wherein the discharge port is a tapered port having a small diameter portion on the side of the oil supply passage and a large diameter portion on the side of the pump chamber, the cross-sectional area of the small diameter portion of the suction port is A ( m ² ), the number of revolutions of the compressor is N (rps), and the volume change per revolution of the oil supply pump is V (m ³ ), so that N · V / A> 1.0 An oil supply device for a horizontal compressor, characterized in that the cross-sectional area of the small diameter part is set. 2. The oil supply device for a horizontal compressor according to claim 1, wherein an opening is provided at an upper portion of the oil supply passage, the opening being open to the space inside the closed container. 3. An oil supply device for a horizontal compressor according to any one of claims 1 and 2, wherein the lubricating oil is an oil in which a fluorine-based refrigerant is dissolved.