CN113266570B - Horizontal rotary compressor - Google Patents

Abstract

The invention provides a horizontal rotary compressor which can effectively separate oil-containing refrigerant gas into oil and refrigerant gas in a closed container, and can supply refrigerant gas with high circulation quantity. The division part divided by the second pressure control plate (41) is deviated to the position of the part passing through the refrigerant discharge pipe (40) in the length direction of the closed container (2), and the second pressure control plate (41) is extended to the inner peripheral surface side of the closed container (2) and is approximately arc-shaped.

Description

Horizontal rotary compressor

Technical Field

The present invention relates to a horizontal rotary compressor that discharges refrigerant gas compressed by a rotary compression element in a closed casing, once together with lubricating oil, to an electric element side in the closed casing, and then to the outside of the closed casing.

Background

Currently, such horizontal rotary compressors are constituted by: the refrigerant gas is sucked into the low-pressure chamber side of the cylinder from the suction port of the rotary compression element, compressed by the operation of the roller and the vane, discharged into the sealed container from the high-pressure chamber side of the cylinder through the discharge port and the exhaust muffler chamber, and then flows into an external radiator or the like.

Further, the bottom portion in the closed casing serves as an oil sump, and lubricating oil is sucked up from the oil sump by an oil pump (oil feed unit) attached to the side opposite to the electric element of the rotary compression element and supplied to the rotary compression element to prevent wear of the rotary compression element.

In such a horizontal rotary compressor, the oil is mixed into the refrigerant gas compressed by the rotary compression element, and the oil is also discharged into the sealed container together with the refrigerant gas.

In order to promote oil separation in the refrigerant gas, the refrigerant gas is once discharged from the rotary compression element to the electric element side of the cylinder, and further rotated from the electric element side to the rotary compression element side in the closed casing. The refrigerant gas is then discharged to the outside through a refrigerant discharge pipe provided in the upper portion of the sealed container, which is a portion on the oil pump side.

Therefore, since the oil is accumulated not only on the oil pump side but also on the electric element side, there is a disadvantage that the oil cannot be smoothly sucked when the oil level of the oil pump portion is lowered.

In order to align the height of the oil level on both the oil pump side and the electromotive element side without the above-described disadvantage of oil accumulation, a device for generating a pressure difference is proposed in which the pressure of the refrigerant gas on the electromotive element side in the closed container is increased and the pressure of the refrigerant gas on the oil pump side is reduced.

This technique is shown in patent document 1. In patent document 1, in order to form a pressure difference between the electric element side and the oil pump side, an annular pressure control plate as a partition plate is provided in a portion of the rotary compression element on the electric element side, and a substantially arc-shaped pressure control plate as a partition plate is similarly provided in a portion of the rotary compression element on the oil pump side.

The annular pressure control plate provided on the electromotive element side of the rotary compression element in patent document 1 partially divides the upper portion of the closed casing into the electromotive element side and the rotary compression element side. Specifically, the outer periphery of the annular pressure control plate is close to the inner surface of the closed casing, and the gap between the annular pressure control plate and the closed casing is defined as a space for forming a differential pressure when the oil-containing refrigerant gas, i.e., the fluid, passes from the electromotive element side toward the rotary compression element side.

The substantially arc-shaped pressure control plate provided on the oil pump side of the rotary compression element partially divides a portion extending from the rotary compression element side to the end portion side of the sealed container in the upper portion of the sealed container partitioned by the annular pressure control plate into the rotary compression element side and the oil pump side. Specifically, the outer edge of the pressure control plate on the side of the closed casing is close to the inner surface of the closed casing, and the gap between the pressure control plate and the closed casing is formed as a space for creating a pressure difference when the fluid passes from the rotary compression element side toward the oil pump side.

In this way, the annular pressure control plate is provided on the electric element side of the rotary compression element, the substantially arc-shaped pressure control plate is provided on the oil pump side, and the fluid composed of the refrigerant gas containing oil passes through the gap along the outer edges of the two pressure control plates in order, thereby increasing the pressure on the electric element side and decreasing the pressure on the oil pump side.

In the horizontal rotary compressor including the pressure control plate, the oil-containing refrigerant gas discharged from the rotary compression element to the electric element side is guided to the upper side of the electric element. The refrigerant gas guided to the upper portion of the electric element passes through the gap around the annular pressure control plate and further passes through the gap between the open portion on the side of the substantially arc-shaped pressure control plate and the closed casing, and when passing through the gap, the oil and the refrigerant gas are separated.

Further, since a pressure difference is formed between the electric element side and the oil pump side, the oil separated and dropped to the oil sump moves to the oil pump side of the bottom of the hermetic container, and the oil level of the oil accumulated on the oil pump side is increased, and the oil pump can smoothly suck the oil. The refrigerant gas is also discharged to the outside of the sealed container from a refrigerant discharge pipe attached to the upper portion of the sealed container on the oil pump side.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2003-269356

Disclosure of Invention

Technical problem to be solved by the invention

The existing horizontal rotary compressor is mostly used for low-temperature application, and the circulating amount of a refrigerant is small. Therefore, oil discharge from the horizontal rotary compressor to the outside is not generally regarded as a problem, and the oil discharged to the outside of the compressor can be handled on the refrigerant utilization equipment side.

In recent years, however, in compressors used for air conditioning applications, there is an increasing need to supply a refrigerant gas in a high circulation amount. In addition, in order to increase the circulation amount by using a DC inverter, the compressor is required to be compact.

However, in the conventional horizontal rotary compressor, conditions such as the position of the refrigerant discharge pipe effective for separating refrigerant gas and oil for effective oil separation, the shape and position of the pressure control plate, and the distance from the rotary compression element to the end of the closed container on the oil pump side are not limited, and there is a limit to effectively separating refrigerant gas and oil in a limited space in the compressor.

In view of the above circumstances, an object of the present invention is to provide a horizontal rotary compressor which is compact and can supply a refrigerant gas at a high circulation rate, and which can efficiently separate an oil-containing refrigerant gas into oil and the refrigerant gas in a closed container.

Technical scheme for solving technical problem

(invention of the first aspect)

The present invention has been made in view of the above problems, and provides a horizontal rotary compressor, comprising: an electrically powered element; a rotary compression element driven by the electrically powered element; a lubricating oil contained in an oil sump at an inner bottom portion of the closed container; and an oil pump provided on the opposite side of the rotary compression element from the electric element for supplying the oil to the rotary compression element, a refrigerant discharge pipe being provided in an upper portion of the closed container on the oil pump side,

an upper portion of the closed casing is partially divided into an electromotive element side and a rotary compression element side by an annular first pressure control plate disposed in a portion of the rotary compression element on the electromotive element side, and a substantially annular first fluid passage portion is formed along an outer side of the first pressure control plate,

an upper portion of the hermetic container on the rotary compression element side is partially divided into a rotary compression element side and an oil pump side by a second pressure control plate having a substantially arc shape disposed in a portion on the oil pump side of the rotary compression element, and an arc-shaped second fluid passage portion is formed along an outer side of the second pressure control plate,

the partition portion defined by the second pressure control plate is biased toward a position where the refrigerant discharge pipe is disposed in a longitudinal direction of the closed casing.

(invention of the second aspect)

In the present invention, it is preferable that a ratio (Dm/Dup) of an outer diameter (Dup) of the first pressure control plate and an outer diameter (Dm) of the first fluid passage portion is set to

1＜Dm/Dup＜1.05，

The ratio (Dlow/Dlow) of the outer diameter (Dlow) of the ring of the second pressure control plate along the outer edge of the sealed container and the inner diameter (Dc) of the sealed container is set as

1＜Dc/Dlow＜1.05，

The ratio (y/x) of the distance (x) from the second pressure control plate to the center of the refrigerant discharge pipe and the distance (y) from the second pressure control plate to the inner end position of the closed container on the oil pump side is set as

3＜y/x＜15，

The ratio (d/x) of the distance (x) from the second pressure control plate to the center of the refrigerant discharge pipe and the inner diameter (d) of the refrigerant discharge pipe is set as

0.5＜d/x＜3，

The second pressure control plate is located on an upstream side in a fluid flow direction than a portion where a refrigerant discharge pipe is provided.

Effects of the invention

(effect of the invention of the first aspect)

According to the invention of the first aspect, the following excellent effects can be achieved: since the partition portion of the second pressure control plate is biased toward the position where the refrigerant discharge pipe is disposed so as to pass through the portion in the longitudinal direction of the sealed container, the refrigerant gas separated by the oil passing through the first fluid passing portion and the second fluid passing portion immediately reaches the refrigerant discharge pipe portion and enters the refrigerant discharge pipe, and the ratio of the oil contained in the refrigerant gas discharged to the outside of the sealed container can be efficiently reduced.

(effect of the second aspect)

According to the invention of the second aspect, the following excellent effects can be achieved: the ratio of oil contained in the refrigerant gas discharged to the outside of the closed casing can be reduced very efficiently.

Drawings

Fig. 1 is an explanatory view schematically showing the movement of oil and refrigerant gas in a horizontal rotary compressor according to an embodiment of the present invention at a radial sectional position of a-a line of fig. 2.

Fig. 2 is an explanatory diagram showing a state of the embodiment viewed from the oil pump side.

Fig. 3 is a diagram showing the rotary compression element, fig. 3 (a) is an explanatory diagram showing a state in which the second pressure control plate is viewed from the oil suction pipe side, fig. 3 (b) is an explanatory diagram showing a state in which the rotary compression element is viewed from a direction intersecting the rotation axis direction, and fig. 3 (c) is an explanatory diagram showing a state in which the first pressure control plate is viewed from the front.

Fig. 4 is a view showing the first pressure control plate, fig. 4 (a) is an explanatory view showing a state seen from one surface side, and fig. 4 (b) is an explanatory view showing a cross section.

Fig. 5 is a view showing the second pressure control plate and the exhaust muffler plate, fig. 5 (a) is an explanatory view showing a state seen from one surface side, and fig. 5 (b) is an explanatory view showing a cross section along a line a-a of fig. 5 (a).

Fig. 6 is an enlarged explanatory view of a part of a radial cross-sectional position of a-a line in fig. 2.

Detailed Description

The present invention will be described in detail below based on embodiments. In the figure, reference numeral 1 denotes a horizontal rotary compressor, and as shown in fig. 1, the horizontal rotary compressor 1 includes an elongated cylindrical sealed container 2 sealed at both ends, and an inner bottom portion of the sealed container 2 is used as an oil sump. A rotary compression element (rotary compression mechanism) 7 including an electric element 3, a first rotary compression element 5 driven by a rotary shaft 4 of the electric element 3, and a second rotary compression element 6 is housed inside the closed casing 2. Fig. 1 schematically shows the structure of the embodiment at a cross-sectional position along the line a-a of fig. 2, and for convenience of explanation, the cross-sectional position is partially changed and shown as shown in fig. 2.

(electric element)

A circular mounting hole 8 is formed in the end of the sealed container 2 on the electric element 3 side. A terminal 9 for supplying electric power to the electromotive element 3 is mounted in the mounting hole 8.

The motor element 3 includes a stator 10 annularly mounted along the inner peripheral surface of the sealed container 2, and a rotor 11 rotatably inserted into the stator 10 with a slight gap provided inside the stator 10. The rotor 11 is fixed to a rotating shaft 4 extending in the longitudinal direction of the sealed container 2 through the center of the rotor 11.

The stator 10 includes a laminated body formed by laminating circular electromagnetic steel plates, and a stator coil wound around a tooth portion of the laminated body by a series winding (concentrated winding) method. The rotor 11 is also formed of a laminated body of electromagnetic steel plates, like the stator 10.

(oil pump)

An oil pump 13 as an oil supply unit is formed at an end portion of the rotary compression element 7 constituted by the first rotary compression element 5 and the second rotary compression element 6 on the opposite side to the electromotive element 3, that is, on the rotary compression element 7 side of the rotary shaft 4.

The oil pump 13 sucks up the lubricating oil 14 from an oil sump formed by the inner bottom portion of the closed casing 2, supplies the lubricating oil to the sliding portions of the first rotary compression element 5 and the second rotary compression element 6 of the rotary compression element 7, and is provided for preventing wear. An oil suction pipe 15 extends from the oil pump 13 toward the inner bottom of the hermetic container 2, and the lower end of the oil suction pipe 15 opens in the oil sump.

(rotating compressing element)

The first rotary compression element 5 has a first cylinder 16 and the second rotary compression element 6 has a second cylinder 17. The intermediate partition plate 18 is located between the first cylinder 16 and the second cylinder 17, and the intermediate partition plate 18 is sandwiched by the first cylinder 16 and the second cylinder 17. That is, the rotary compression element (rotary compression mechanism) 7 includes the first rotary compression element 5, the second rotary compression element 6, and the intermediate partition plate 18.

The first and second rotary compression elements 5 and 6 are constituted by: first and second cylinders 16, 17 respectively disposed on both sides (left and right in fig. 1) of the intermediate partition plate 18; first and second rollers 21 and 22 fitted to first and second eccentric portions 19 and 20 provided on the rotary shaft 4 with a phase difference of 180 degrees and eccentrically rotating in the first and second cylinders 16 and 17; blades, not shown, which are in contact with the rollers 21 and 22 and partitioned into a low pressure chamber side and a high pressure chamber side in the first and second cylinders 16 and 17, respectively; a main bearing 23 and a sub bearing 24 which close the opening surface of the first cylinder 16 on the electric element 3 side and the opening surface of the second cylinder 17 on the side opposite to the electric element 3 (on the oil pump 13 side) and serve as bearings for the rotary shaft 4.

The first cylinder 16 is provided with a suction passage 25 communicating with the low-pressure chamber side inside the first cylinder 16 through a suction port. Further, the second cylinder 17 and the intermediate partition plate 18 are also provided with a suction passage 26 communicating with the low-pressure chamber side inside the second cylinder 17 through the suction port.

These suction passages 25, 26 are constructed to communicate with one end of a refrigerant introduction pipe 27, which will be described later, and refrigerant gas is supplied from the refrigerant introduction pipe 27 through the respective suction passages 25, 26 and suction ports into the first and second cylinders 16, 17.

(exhaust anechoic chamber)

The refrigerant gas compressed in the first and second cylinders 16 and 17 is discharged through discharge ports formed in the main bearing 23 and the sub bearing 24 to discharge muffling chambers 28 and 29 formed on the electromotive element 3 side of the main bearing 23 and the opposite side of the sub bearing 24 from the electromotive element 3, respectively.

An exhaust muffler plate 30 having an opening centered on a portion of the main bearing 23 through which the bearing portion of the rotary shaft 4 passes is attached to the main bearing 23 so as to cover the periphery of the bearing portion, thereby forming an exhaust muffler chamber 28 on the electromotive element 3 side. The high-pressure side of the first cylinder 16 communicates with the exhaust muffler chamber 28 via a through hole formed in the main bearing 23.

Further, a cup-shaped exhaust muffler plate 31 is attached to the sub-bearing 24 so as to cover the sub-bearing 24 including the bearing portion of the sub-bearing 24 from the oil pump 13 side, thereby forming a discharge muffler chamber 29 on the oil pump 13 side. As shown in the drawing, a mounting hole in which the oil suction pipe 15 of the oil pump 13 is mounted is provided at the center of the exhaust muffler plate 31. The high-pressure side of the second cylinder 17 communicates with the discharge muffling chamber 29 through a through hole formed in the sub-bearing 24.

The exhaust muffler chamber 28 and the exhaust muffler chamber 29 communicate with each other through a communication passage (not shown) that penetrates the first and second cylinders 16 and 17 (plate portions of the cylinders) and the intermediate partition plate 1 and is opened into the exhaust muffler chamber 28. In fig. 6, reference numeral 32 denotes an end of the communication passage on the exhaust muffler chamber 28 side, and is a through hole formed in the cylinder corresponding portion of the main bearing 23.

When the rotary compression element 7 is operated, the high-pressure refrigerant gas compressed by the second rotary compression element 6 is discharged to the discharge muffler chamber 28 through the discharge muffler chamber 29 and the communication passage. The high-pressure refrigerant gas compressed by the first rotary compression element 5 is discharged to the exhaust muffler chamber 28, merges with the high-pressure refrigerant gas compressed by the second rotary compression element 6, passes through between the opening portion of the exhaust muffler plate 30 through which the bearing portion of the main bearing 23 passes and the bearing portion, and is discharged to the electromotive element 3 side.

At this time, the oil supplied to the first and second rotary compression elements 5 and 6 is mixed into the refrigerant gas, and the oil is also discharged to the electric element 3 side in the closed casing 2. The oil mixed in the refrigerant gas is thereafter separated from the refrigerant gas and accumulated in an oil pool at the inner bottom of the closed casing 2.

(rotating shaft)

An oil passage, not shown, is provided on the rotation axis 4 on the rotation center line, and extends from the end portion side of the rotation axis 4 supported by the sub-bearing 24 toward the electromotive element 3. Further, the oil pump 13 has a known structure as follows: on the end portion side of the oil passage supported by the sub-bearing 24, the oil is guided toward the electromotive element 3 side, and the oil is sucked from the oil suction pipe 15 side.

Further, a small hole is provided in the rotary shaft 4, through which oil is guided to the first and second rotary compression elements 5, 6 and the bearing portions of the main bearing 23 and the sub bearing 24, and the small hole communicates with the oil passage. Oil is supplied to the first rotary compression element 5 and the second rotary compression element 6 and the bearing portions of the main bearing 23 and the sub bearing 24 via the oil passage of the rotary shaft 4 and the small hole, and lubricates them.

Therefore, as described above, the oil supplied to the first and second rotary compression elements 5 and 6 is mixed into the refrigerant gas, and the fluid composed of the oil-containing refrigerant gas is discharged to the electric element 3 side in the closed casing 2. In the horizontal rotary compressor 1, oil is separated from the fluid discharged to the electromotive element 3 side, the separated oil is collected in an oil sump, and the compressed refrigerant gas, which is the oil-separated fluid, is discharged to the outside of the closed casing 2.

(pressure control plate)

In addition, in the horizontal rotary compressor 1 of the present embodiment, a differential pressure is formed at the time of oil separation, the pressure of the space on the electric element 3 side of the hermetic container 2 is increased, and the pressure of the space on the oil pump 13 side is decreased, whereby the oil level height of the oil sump on the oil pump 13 side is increased, and the oil pump 13 appropriately performs oil suction. Further, the oil is efficiently separated, and the refrigerant gas is discharged to the outside of the closed casing 2.

In order to form the above-described differential pressure at the time of oil separation, the horizontal rotary compressor 1 includes pressure control plates on the electric element 3 side and the oil pump 13 side of the rotary compression element 7.

(first pressure control plate)

In the present embodiment, the first pressure control plate 33 is disposed on the electromotive element 3 side of the first rotary compression element 5. The first pressure control plate 33 is formed along the outer periphery of the exhaust muffler chamber 28, and is formed of an annular steel plate as shown in fig. 4. Two attachment pieces 34 protruding toward the center of the opening portion are provided in the central opening portion into which the exhaust muffler plate 30 forming the exhaust muffler chamber 28 is fitted, and the attachment pieces 34 are overlapped with the exhaust muffler plate 30 and screwed to the main bearing 23 together with the exhaust muffler plate 30.

The exhaust muffler plate 30 is made of the same steel material as the first pressure control plate 33.

As shown in fig. 4, the outer edge 35 of the annular first pressure control plate 33 is formed in a circular shape substantially over the entire circumference. In fig. 3 (c) and 4 (a), a part of the outer edge forms a straight edge in order to avoid interference with other parts and the like at the time of assembling the compressor. The portion that becomes the edge of the straight line includes a portion submerged in the oil pool.

The main bearing 23 to which the exhaust muffler plate 30 and the first pressure control plate 33 are attached includes a plate portion 36 extending radially around the bearing portion and a flange 37 continuous with the plate portion 36, and the flange 37 penetrates the inner peripheral surface of the closed casing 2 and is in close contact therewith. As shown in fig. 1 and 6, the flange 37 is provided to extend from the outer peripheral position of the plate portion 36 toward the motor element 3 side at a substantially L-shaped cross-sectional portion formed by the plate portion 36 and the flange 37 around the bearing portion of the main bearing 23.

The exhaust muffler plate 30 and the first pressure control plate 33 are attached from the electromotive element 3 side of the main bearing 23, and the outer edge 35 of the first pressure control plate 33 is close to the inner peripheral surface of the flange 37 with a gap therebetween.

Since the circular outer edge 35 of the first pressure control plate 33 is close to the inner peripheral surface of the flange 37 of the main bearing 23 with a gap therebetween, the upper portion of the first pressure control plate 33 in the closed casing 2 is partially divided into the motor element 3 side and the rotary compression element 7 side in a state of being disposed in the motor element side portion of the rotary compression element 7. The part not partitioned is between the outer edge 35 of the first pressure control plate 33 and the inner circumferential surface 38 of the flange 37.

Further, a portion between the outer edge 35 of the undivided first pressure control plate 33 and the inner circumferential surface 38 of the flange 37 is a portion through which a fluid made of an oil-containing refrigerant gas can pass from the electromotive element 3 side toward the rotary compression element 7 side. Thus, in the horizontal rotary compressor 1 of the present embodiment, the first pressure control plate 33 partially divides the upper portion of the inside of the closed casing 2 into the electric element 3 side and the rotary compression element 7 side, and the substantially annular first fluid passage portion 39 constituted by the gap is formed along the outer edge 35 of the first pressure control plate 33.

The substantially annular first fluid passage portion 39 is formed at a distance sufficiently large enough to form a slight pressure difference between the electromotive element 3 side and the rotary compression element 7 side by the flow of the fluid made of the refrigerant gas containing oil.

The plate portion 36 of the main bearing 23 is provided with a plurality of openings wide enough not to interfere with the movement of the fluid composed of the oil-containing refrigerant gas and the movement of the oil in the oil pool, and even if the oil-containing gas, i.e., the refrigerant gas, passes through the openings, a pressure difference is not formed in the opening portion.

The refrigerant gas (oil-containing fluid) compressed by the first and second rotary compression elements 5 and 6 and discharged from the discharge muffler chamber 28 to the space where the electromotive element 3 is located passes through the first fluid passage portion 39, and thus, as described above, a slight pressure difference is formed, but the fluid flowing through the space on the electromotive element 3 side flows to the rotary compression element 7 side without support.

(second pressure control plate)

In the horizontal rotary compressor 1 of the present embodiment, as shown in fig. 2, a refrigerant discharge pipe 40 is provided from the top of the sealed container 2 to the side of the container in the girth direction. As described above, the horizontal rotary compressor 1 also includes the pressure control plate at the oil pump 13 side of the rotary compression element 7, and the position of the pressure control plate in the girth direction corresponds to the position of the refrigerant discharge pipe 40.

In the present embodiment, a pressure control plate corresponding to the position of the refrigerant discharge pipe 40 in the girth direction of the sealed container 2 is provided on the oil pump 13 side of the rotary compression element 7 as a second pressure control plate 41 disposed on a part of the outer periphery of the exhaust muffling chamber 29.

As shown in fig. 5, the second pressure control plate 41 is formed of a steel plate integrated with the exhaust muffler plate 31 forming the exhaust muffler chamber 29. The second pressure control plate 41 is formed in a substantially arc shape and extends from the second rotary compression element 6 side toward the closed casing 2, and an outer edge 43 on the closed casing 2 side is close to an inner peripheral surface 42 of the closed casing 2 with a gap therebetween.

Since the outer edge 43 of the second pressure control plate 41 facing the inner peripheral surface 42 side of the closed casing 2 is close to the closed casing 2 with a gap therebetween, the second pressure control plate 41 partially divides the upper portion of the closed casing 2 into the rotary compression element 7 side and the oil pump 13 side in a state of being disposed in the oil pump 13 side portion of the rotary compression element 7. The non-partitioned portion is a portion between the outer edge 43 of the second pressure control plate 41 and the inner peripheral surface 42 of the closed casing 2, and the second pressure control plate 41 itself is not present in the girth direction passing through the second pressure control plate 41.

On the lower portion side of the closed vessel of the exhaust muffler plate 31 itself integrated with the second pressure control plate 41, there is no portion protruding to hinder the movement of oil, and the lower portion of the exhaust muffler plate 31 is directly immersed in the oil sump.

A portion between the outer edge 43 of the undivided second pressure control plate 41 and the inner circumferential surface 42 of the closed casing 2 is a portion through which a fluid made of an oil-containing refrigerant gas can pass from the space on the rotary compression element 7 side to the space on the oil pump 13 side.

Thus, in the horizontal rotary compressor 1 of the present embodiment, the second pressure control plate 41 partially divides the upper portion of the closed casing 2 into the rotary compression element 7 side and the oil pump 13 side, and a substantially arc-shaped second fluid passage portion 44 formed by a gap is formed in a portion along the outer edge 43 of the second pressure control plate 41.

(position of second fluid passing portion)

As described above, the second fluid passage portion 44 having a substantially arc shape is a portion constituted by the gap between the outer edge 43 of the second pressure control plate 41 and the inner peripheral surface 42 of the sealed container 2, and the position of the second pressure control plate 41 itself, which is the dividing portion of the second pressure control plate 41, is biased in the girth direction of the sealed container 2 so as to correspond to the position of the refrigerant discharge pipe 40, so that the position of the second fluid passage portion 44 is also biased in the longitudinal direction of the sealed container 2 so as to pass through the portion where the refrigerant discharge pipe 40 is disposed.

The second fluid passage portion 44 is formed in a substantially arc shape at a distance sufficiently large enough to form a slight pressure difference between the rotary compression element 7 side and the oil pump 13 side by the flow of the fluid made of the refrigerant gas containing oil.

The refrigerant gas compressed by the first and second rotary compression elements 5 and 6 and passed through the space on the electric element 3 side and the space on the upper side of the rotary compression element 7 discharged from the first fluid passage portion 39 is discharged to the space on the oil pump 13 side through the second fluid passage portion 44, thereby forming a slight pressure difference. Of course, even when the fluid passes through the second fluid passage portion 44, the fluid can flow into the space on the oil pump 13 side without support.

The pressure difference created by the fluid flowing through the second fluid passage portion 44 also acts as follows: the pressure of the space on the electric element 3 side of the closed casing 2 is increased, and the pressure of the space on the oil pump 13 side is decreased. Further, it contributes to increase in the height of the oil level of the oil pool on the oil pump 13 side, and oil suction by the oil pump 13 is appropriately performed.

Further, when the fluid flows through the second fluid passage portion 44, oil separation is efficiently performed, and the refrigerant gas after oil separation moves toward the portion where the refrigerant discharge pipe 40 is attached, and further, since the second fluid passage portion 44 is disposed on the line through which the refrigerant discharge pipe 40 passes in the longitudinal direction of the closed casing 2, the refrigerant gas after oil separation easily enters the refrigerant discharge pipe 40, and the refrigerant gas after oil separation is discharged.

The oil stored in the oil pool at the bottom in the closed casing 2 is moved to the oil pump 13 side by the pressure difference formed by the fluid flowing through the first fluid passing portion 39 and the second fluid passing portion 44, and the oil level at the oil pump 13 side is raised. Thus, the opening of the end portion of the oil suction pipe 15 is immersed in the oil without hindrance, so that the oil can be smoothly supplied to the sliding portion of the rotary compression element (rotary compression mechanism portion) 7 of the oil pump 13.

Further, the first pressure control plate 33 and the second pressure control plate 41 cause a difference in pressure between the electric element 3 side and the oil pump 13 side, the electric element 3 side being high and the oil pump 13 side being low, and the oil accumulated on the electric element 3 side can also move to the oil pump 13 side.

This ensures the oil level on the oil pump 13 side and ensures the oil supply, and the oil having good heat conduction can cool the electric element 3. Therefore, the operation performance of the electromotive element 3 and the flow of the refrigerant gas can be improved, and the respective performances of the compressor, i.e., the suction, compression, and discharge of the refrigerant gas, can be ensured.

Further, the refrigerant gas discharged into the closed casing 2 easily reaches the portion where the refrigerant discharge pipe is attached through the first fluid passage portion and the second fluid passage portion, and flows toward the refrigerant discharge pipe 40 while effectively separating the oil mixed in the refrigerant gas, so that the amount of oil discharged to the outside of the closed casing 2 through the refrigerant discharge pipe 40 can be greatly reduced.

(Condition restriction)

In the horizontal rotary compressor 1 of the embodiment, conditions such as the distance and the position of each part are defined so that oil can be separated more effectively. The dimensional ranges of the respective portions for defining the conditions are shown in fig. 6. Note that, in fig. 6, only a cross section of a part of the horizontal rotary compressor 1 at a position along the cross section line of fig. 2 is shown.

Ratio (Dm/Dup)

First, in the horizontal rotary compressor 1, the ratio (Dm/Dup) of the outer diameter (Dup) of the first pressure control plate 33 and the outer diameter (Dm) of the first fluid passage portion 39 is set to

1＜Dm/Dup＜1.05。

Ratio (Dc/Dlow)

Next, the ratio (Dlow/Dlow) of the outside diameter (Dlow) of the ring of the second pressure control plate 41 along the outer edge 43 on the side of the sealed container 2 to the inside diameter (Dc) of the sealed container 2 is set to

1＜Dc/Dlow＜1.05。

As described above, the outer edge 43 of the second pressure control plate 41 is arc-shaped, but the outer edge 43 is assumed to be a virtual ring extending in the inner circumferential direction of the closed casing 2. The outer diameter of the ring is set to (Dlow).

Ratio (y/x)

Next, the ratio (y/x) of the distance (x) from the second pressure control plate 41 to the center of the refrigerant discharge pipe 40 and the distance (y) from the second pressure control plate 41 to the inner end position of the closed container 2 on the side of the oil supply member (oil pump 13) is set as

3＜y/x＜15。

Ratio (d/x)

Next, the ratio (d/x) of the distance (x) from the second pressure control plate 41 to the center of the refrigerant discharge pipe 40 and the inner diameter (d) of the refrigerant discharge pipe 40 is set to

0.5＜d/x＜3。

Further, as described above, the second pressure control plate 41 is located on the upstream side in the fluid flow direction from the portion where the refrigerant discharge tube 40 is provided.

In the above range, in the embodiment, it is assumed that:

Dm/Dup＝1.03、

Dc/Dlow＝1.02、

y/x＝4.8、

d/x＝0.8。

the horizontal rotary compressor of the embodiment and the horizontal rotary compressor of the conventional product, both of which had been set under the above conditions, used 1000W of power, and the oil discharge amounts of the refrigerant discharge pipes were compared.

(results)

In the prior art horizontal rotary compressor, the oil discharge amount (mL/min) was 7.6/25 at an operating frequency of 60/80 (rps). On the other hand, in the horizontal rotary compressor of the present embodiment, the oil discharge amount is 3.3/13.3 at an operating frequency of 60/80 (rps) as well.

From the above comparison, it was confirmed that in the horizontal rotary compressor 1 of the embodiment, the refrigerant gas and the oil are separated in the closed casing 2, and the oil discharge amount of the refrigerant discharge pipe 40 is reduced by about 60% as compared with the conventional product.

Description of the reference numerals

1 … horizontal rotary compressor,

2 … the container is closed,

3 … motorized element,

4 … rotates a shaft,

5 … a first rotary compression element,

6 … a second rotary compression element,

7 … rotates the compression element,

13 … oil pump,

14 … oil,

15 … oil suction pipe,

16 … a first cylinder,

17 … a second cylinder,

23 … is a main bearing,

24 … secondary bearing,

27 … a refrigerant introducing pipe,

30 … air exhaust silencing plate,

31 … exhaust muffler plate,

33 … a first pressure control plate,

35 … outer edge,

36 … a plate portion of a main bearing,

37 … a flange of a main bearing,

38 …,

39 … a first fluid passing portion,

a 40 … refrigerant discharge tube,

41 … a second pressure control plate,

42 … seals the inner peripheral surface of the container,

43 … the outer edge of the second pressure control plate,

44 … a second fluid passage.

Claims (2)

1. A horizontal rotary compressor is characterized in that,

a horizontal closed container is provided with: an electrically powered element; a rotary compression element driven by the electrically powered element; a lubricating oil contained in an oil sump at an inner bottom portion of the closed container; and an oil pump provided on the opposite side of the rotary compression element from the electric element for supplying the lubricating oil to the rotary compression element, a refrigerant discharge pipe being provided in an upper portion of the closed container on the oil pump side,

an upper portion of the closed casing is partially divided into an electromotive element side and a rotary compression element side by an annular first pressure control plate disposed in a portion of the rotary compression element on the electromotive element side, and a substantially annular first fluid passage portion is formed along an outer side of the first pressure control plate,

an upper portion of the hermetic container on the rotary compression element side is partially divided into a rotary compression element side and an oil pump side by a second pressure control plate of a substantially arc shape disposed at a portion on the oil pump side of the rotary compression element, and an arc-shaped second fluid passage portion is formed along an outer side of the second pressure control plate,

a partition portion defined by the second pressure control plate is biased toward a position where the refrigerant discharge pipe is disposed in a longitudinal direction of the closed casing;

a ratio Dm/Dup of an outer diameter Dup of the first pressure control plate and an outer diameter Dm of the first fluid passing portion is set to 1 < Dm/Dup < 1.05,

the ratio Dlow/Dlow between the outside diameter Dlow of the ring of the second pressure control plate along the outer edge on the side of the sealed container and the inside diameter Dc of the sealed container is set to 1 < Dc/Dlow < 1.05,

the ratio y/x of the distance x from the second pressure control plate to the center of the refrigerant discharge pipe and the distance y from the second pressure control plate to the inner end position of the oil pump side of the hermetic container is set to 3 < y/x < 15,

the ratio d/x between the distance x from the second pressure control plate to the center of the refrigerant discharge tube and the inner diameter d of the refrigerant discharge tube is set to 0.5 < d/x < 3.

2. The horizontal type rotary compressor according to claim 1,

the second pressure control plate is located on an upstream side in a fluid flow direction than a portion where a refrigerant discharge pipe is provided.

Images