Horizontal rotary compressor

Abstract

To minimize a degree to which refrigerant gas containing oil is discharged to the outside of a closed container, to resolve failure due to decrease in oil amount in the closed container, in a horizontal rotary compressor.SOLUTION: A horizontal closed container 2 comprises: an electric element 4; a rotary compression element 8; lubricating oil f stored in an oil reservoir 3 of the closed container 2; an oil pump 13 that supplies the oil f to the rotary compression element; a substantially annular fluid passage part 39 formed on the electric element 4 side of the rotary compression element 8; and a refrigerant discharge pipe 40 located at the upper part of the closed container 2 on the oil pump 13 side. The refrigerant discharge pipe 40 has an extension pipe part 46, and the extension pipe part 46 is provided with a plurality of through holes 48.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a horizontal rotary compressor configured to discharge refrigerant gas compressed by a rotary compression element in a sealed container together with lubricating oil once to the electric element side in the sealed container and then discharge it outside the sealed container.

[0002] Conventionally, in this type of horizontal rotary compressor, refrigerant gas is inhaled from the suction port of the rotary compression element to the low-pressure chamber side of the cylinder, compressed by the operation of the roller and the vane, and discharged into the sealed container through the discharge port and the discharge silencer chamber on the high-pressure chamber side of the cylinder. Thereafter, it is configured to flow into an external radiator or the like.

[0003] Also, the bottom of the sealed container is an oil reservoir, and lubricating oil is sucked up from the oil reservoir by an oil pump (oil supply means) 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.

[0004] 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.

[0005] 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 circulated in the sealed container from the electric element side to the rotary compression element side. And the discharge of the refrigerant gas to the outside is performed from a refrigerant discharge pipe provided at a portion on the oil pump side at the upper part of the sealed container.

[0006] Therefore, the oil accumulates not only on the oil pump side but also on the electric element side, so that when the oil level in the oil pump portion drops, a problem occurs that the oil cannot be smoothly sucked.

[0007] As mentioned above, if the oil levels on both the oil pump side and the electric element side become equal, the oil level in the oil reservoir on the oil pump side will drop, making it difficult to draw oil smoothly. To prevent this problem, a method has been proposed to create a pressure difference by increasing the pressure of the refrigerant gas on the electric element side within the sealed container and decreasing the pressure of the refrigerant gas on the oil pump side.

[0008] This technology is described in Patent Document 1. Patent Document 1 relates to a horizontal rotary compressor, and as shown in Figure 10, the horizontal rotary compressor a comprises an electric element c, a rotary compression element d driven by the electric element c, lubricating oil f contained in an oil reservoir e at the bottom of the sealed container b, and an oil supply means (oil pump g) for supplying the oil f to the rotary compression element d.

[0009] Furthermore, in order to create a pressure difference between the electric element c side and the oil pump g side, an annular pressure control plate i is provided on the electric element c side of the rotary compression element d, which acts as a baffle plate to restrict the flow of refrigerant gas h containing oil f, and a roughly arc-shaped pressure control plate j is provided on the oil pump g side of the rotary compression element d, which also acts as a baffle plate.

[0010] The annular pressure control plate i provided on the electric element c side of the rotary compression element d in Patent Document 1 partially divides the upper part of the sealed container b into the electric element c side and the rotary compression element d side. Specifically, the outer circumference of the annular pressure control plate i is close to the inner surface of the sealed container b, and the gap between the annular pressure control plate i and the sealed container b is such that a differential pressure is formed when the refrigerant gas h containing oil f passes from the electric element c side to the rotary compression element d side.

[0011] Furthermore, the substantially arc-shaped pressure control plate j provided on the oil pump g side of the rotating compression element d partially divides the portion of the sealed container b, which is partitioned by the annular pressure control plate i, from the rotating compression element d side to the end of the sealed container b, into the rotating compression element d side and the oil pump g side. Specifically, the outer edge of this pressure control plate j on the sealed container b side is close to the inner surface of the sealed container b, and the gap between the substantially arc-shaped pressure control plate j and the sealed container b is such that a differential pressure is formed when the refrigerant gas h, containing oil f, passes from the rotating compression element d side to the oil pump g side.

[0012] In this configuration, an annular pressure control plate i is provided on the electric element c side of the rotating compression element d, and a substantially arc-shaped pressure control plate j is provided on the oil pump g side. The refrigerant gas h containing oil f passes sequentially through the gaps along the outer edges of both pressure control plates i and j, thereby increasing the pressure on the electric element c side and decreasing the pressure on the oil pump g side.

[0013] In a horizontal rotary compressor a equipped with pressure control plates i and j, the refrigerant gas h containing oil f discharged from the rotary compression element d to the electric element c is guided upwards to the electric element c.

[0014] The refrigerant gas h, guided to the top of the electric element c, passes through the gap around the annular pressure control plate i, and further through the open portion on the side of the roughly arc-shaped pressure control plate j and the gap between it and the sealed container b. As it passes through these gaps, the oil f and refrigerant gas h are separated. In Figure 10, the movement of oil f and refrigerant gas h are indicated by arrows.

[0015] Then, the separated oil f that settles into the oil reservoir e moves to the oil pump g side at the bottom of the sealed container b due to the pressure difference created between the electric element c side and the oil pump g side, and also raises the oil level l of the oil f accumulated on the oil pump g side, allowing the oil pump g to smoothly draw in the oil f.

[0016] Furthermore, a curved refrigerant discharge pipe m is positioned at the top of the sealed container b, which is on the oil pump g side. The lower end of the refrigerant discharge pipe m is attached so that it faces into the sealed container b from the body of the sealed container b. The refrigerant gas h is then discharged to the outside of the sealed container b from the refrigerant discharge pipe m attached to the top of the sealed container b, which is on the oil pump g side. [Prior art documents] [Patent Documents]

[0017] [Patent Document 1] Japanese Patent Publication No. 2003-269356 [Overview of the project] [Problems that the invention aims to solve]

[0018] In a horizontal rotary compressor a, as described above, the refrigerant gas h containing oil f, which is sent from the rotating compression element d towards the electric element c, passes through the upper part of the electric element c in the sealed container b, and is then guided downwards towards the space where the oil pump g is located, passing through the gap formed by the pressure control plates i and j. Furthermore, the refrigerant gas h containing oil f is separated into oil f and refrigerant gas h by passing through the gap formed by the pressure control plates i and j. However, the refrigerant gas h containing some oil f is discharged from the refrigerant discharge pipe m to the outside of the sealed container b.

[0019] In particular, at high power output and high rotation speeds, the oil dissolved in the refrigerant gas is not separated, and the refrigerant gas containing the oil is discharged outside the sealed container through the refrigerant discharge pipe, resulting in a decrease in the amount of oil inside the sealed container.

[0020] Specifically, in inverter-type horizontal rotary compressors for low-temperature applications, the refrigerant circulation volume is low even at high rotation speeds, so the oil discharge volume is also small and was not considered a malfunction. However, in the inverter models of horizontal rotary compressors for high temperatures, the circulation volume of the refrigerant gas increases during high-speed rotation. Also, the differential pressure rises rapidly during high-speed rotation, causing the oil level in the oil reservoir on the oil pump side to rise too much. From this aspect as well, the oil discharge volume increases. Therefore, there was a problem that the amount of oil in the sealed container decreased.

[0021] Therefore, in view of the above circumstances, an object of the present invention is to minimize the degree to which the refrigerant gas containing oil is discharged outside the sealed container in a horizontal rotary compressor, and to solve the problem caused by the decrease in the amount of oil in the sealed container.

Means for Solving the Problems

[0022] The present invention has been made in consideration of the above problems, inside a horizontal sealed container, an electric element, a rotary compression element driven by the electric element, lubricating oil stored in an oil reservoir at the inner bottom of the sealed container, an oil pump provided on the side opposite to the electric element of the rotary compression element for supplying oil to the rotary compression element, the upper part inside the sealed container is partially partitioned into an electric element side and a rotary compression element side by an annular pressure control plate arranged in the part on the electric element side of the rotary compression element, and a substantially annular fluid passage portion formed along the outside of this pressure control plate, a refrigerant discharge pipe located at the upper part on the oil pump side in the sealed container, and is provided with, the refrigerant discharge pipe has an extension pipe portion that extends along the longitudinal direction of the sealed container inside the sealed container and has a closed tip, the extension pipe portion is provided with a plurality of through holes that penetrate and open in a direction along the circumferential direction of the body of the sealed container, and provides a horizontal rotary compressor characterized by this, and solves the above problems.

[0023] Furthermore, in the present invention, it is preferable that the end of the sealed container on the oil pump side is extended in the longitudinal direction of the sealed container, and the oil reservoir space on the oil pump side is enlarged on the side opposite to the electric element side of the rotary compression element.

[0024] Also, in the present invention, it is preferable that the ratio of the circulation amount of the refrigerant gas passing through the sealed container to the total opening area of the through holes of the refrigerant discharge pipe is 500 or less.

[0025] Also, in the present invention, it is preferable that the ratio of the space volume above the oil reservoir in the sealed container to the circulation amount of the refrigerant gas passing through the sealed container is 0.03 or more.

Advantages of the Invention

[0026] According to the present invention, the refrigerant discharge pipe has an extension pipe portion extending along the longitudinal direction of the sealed container inside the sealed container, and the extension pipe portion is provided with a plurality of through holes penetrating and opening in a direction along the circumferential direction of the body portion of the sealed container. Therefore, when the refrigerant gas containing oil enters the through holes opened in the extension pipe portion of the refrigerant discharge pipe, it is separated into oil and refrigerant gas, accumulates in the extension pipe portion, and then flows down to the oil reservoir portion on the oil pump side. As a result, the amount of oil discharged outside the sealed container is suppressed.

[0027] In addition, since the oil reservoir space on the oil pump side of the sealed container is enlarged on the side opposite to the electric element side of the rotary compression element, it becomes possible to suppress the rise of the oil level in the oil reservoir on the oil pump side during the operation of the horizontal rotary compressor. During operation, the oil level in the oil reservoir on the oil pump side does not rise excessively, so that a sufficiently wide space is formed above the oil reservoir on the oil pump side. Therefore, when the refrigerant gas containing oil flows in the space above this oil reservoir, it is easily separated into oil and refrigerant gas. Thus, the amount of oil discharged outside the sealed container is suppressed.

Brief Description of the Drawings

[0028] [Figure 1]This is an explanatory diagram illustrating the movement of oil and refrigerant gas in a horizontal rotary compressor according to an embodiment of the present invention, at radial positions along the line aa and the line bb passing through the refrigerant discharge pipe in Figure 2, and at longitudinal cross-sectional positions of the sealed container. [Figure 2] This is an explanatory diagram showing the embodiment as viewed from the oil pump side. [Figure 3] These diagrams illustrate the rotating compression element. (a) is an explanatory diagram showing the second pressure control plate viewed from the oil suction pipe side, (b) is an explanatory diagram showing the rotating compression element viewed from a direction intersecting the rotation axis, and (c) is an explanatory diagram showing the first pressure control plate viewed from the front. [Figure 4] The first pressure control plate is shown; (a) is an explanatory diagram showing the view from one side, and (b) is an explanatory diagram showing the cross-section. [Figure 5] The second pressure control plate and discharge sound-dampening plate are shown; (a) is an explanatory diagram showing the view from one side, and (b) is an explanatory diagram showing a cross-section along line aa in (a). [Figure 6] This is an explanatory diagram showing an enlarged portion of the radial cross-sectional position along line aa and line bb passing through the refrigerant discharge pipe in Figure 2. [Figure 7] This is an explanatory diagram showing the refrigerant discharge pipe as viewed from the side. [Figure 8] This is an explanatory diagram that shows the correlation between "oil discharge volume" and "refrigerant circulation volume and discharge pipe cross-sectional area ratio" in a graph. [Figure 9] This is an explanatory diagram that shows the correlation between "oil discharge volume" and "the ratio of the oil separation space volume inside the case to the refrigerant circulation volume" in a graph. [Figure 10] This is an explanatory diagram that schematically shows the movement of oil and refrigerant gas in a conventional horizontal rotary compressor at a cross-sectional position along the longitudinal direction of a sealed container. [Modes for carrying out the invention]

[0029] Next, the present invention will be described in detail based on embodiments. In the figure, 1 is a horizontal rotary compressor, and as shown in Figure 1, the horizontal rotary compressor 1 is equipped with a horizontally elongated cylindrical sealed container 2 with both ends sealed, and the inner bottom of this sealed container 2 is an oil reservoir 3. Inside the sealed container 2 is housed an electric element 4 and a rotary compression element (rotary compression mechanism) 8 consisting of a first rotary compression element 6 and a second rotary compression element 7, which are driven by the rotating shaft 5 of the electric element 4. Note that Figure 1 schematically shows the configuration of the embodiment at a position along line aa in Figure 2, and for the sake of ease of explanation, the display position has been partially changed as shown in Figure 2.

[0030] (Electric element) A circular mounting hole 9 is formed at the end of the sealed container 2 on the side facing the electric element 4. A terminal 10 for supplying power to the electric element 4 is attached to the mounting hole 9.

[0031] The electric element 4 consists of a stator 11 mounted annularly along the inner circumferential surface of the sealed container 2, and a rotor 12 rotatably inserted inside the stator 11 with a small gap between them. The rotor 12 is fixed to a rotating shaft 5 that passes through the center of the rotor 12 and extends in the longitudinal direction of the sealed container 2.

[0032] The stator 11 has a laminate made of stacked donut-shaped electromagnetic steel sheets and stator coils wound around the teeth of this laminate using a direct winding (concentrated winding) method. The rotor 12 is also formed from a laminate of electromagnetic steel sheets, similar to the stator 11.

[0033] (Oil pump) An oil pump 13, which is a means of lubrication, is formed on the opposite side of the rotary compression element 8, which consists of a first rotary compression element 6 and a second rotary compression element 7, from the electric element 4, that is, at the end of the rotary shaft 5 on the rotary compression element 8 side.

[0034] The oil pump 13 is provided to draw up lubricating oil 14 from an oil reservoir 3, which is formed using the inner bottom of the sealed container 2, and supply it to the sliding parts of the first rotary compression element 6 and the second rotary compression element 7 in the rotary compression element 8, thereby preventing wear. An oil suction pipe 15 extends from the oil pump 13 toward the inner bottom of the sealed container 2, and the lower end of the oil suction pipe 15 is open inside the oil reservoir 3 (the oil reservoir 3 on the oil pump 13 side).

[0035] (Rotational compression element) The first rotary compression element 6 has a first cylinder 16, and the second rotary compression element 7 has a second cylinder 17. An intermediate partition plate 18 is located between the first cylinder 16 and the second cylinder 17, and the intermediate partition plate 18 is sandwiched between the first cylinder 16 and the second cylinder 17. That is, the rotary compression element (rotary compression mechanism) 8 comprises the first rotary compression element 6, the second rotary compression element 7, and the intermediate partition plate 18.

[0036] The first and second rotating compression elements 6 and 7 each consist of first and second cylinders 16 and 17, respectively, arranged on both sides (left and right in Figure 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 rotating shaft 5 with a 180-degree phase difference and rotating eccentrically inside the first and second cylinders 16 and 17; vanes (not shown) that abut against these rollers 21 and 22 to divide the inside of the first and second cylinders 16 and 17 into a low-pressure chamber side and a high-pressure chamber side, respectively; and main bearings 23 and sub-bearings 24, which also serve as bearings for the rotating shaft 5, closing the opening surface of the first cylinder 16 on the electric element 4 side and the opening surface of the second cylinder 17 on the opposite side of the electric element 4 (oil pump 13 side), respectively.

[0037] The first cylinder 16 has a suction passage 25 that communicates with the low-pressure chamber inside the first cylinder 16 via a suction port. The second cylinder 17 and the intermediate partition plate 18 also have suction passages 26 that communicate with the low-pressure chamber inside the second cylinder 17 via a suction port.

[0038] These suction passages 25 and 26 are connected to one end of a refrigerant introduction pipe 27, which will be described later. Refrigerant gas is supplied from the refrigerant introduction pipe 27 to the first and second cylinders 16 and 17 via the respective suction passages 25 and 26 and the suction port.

[0039] (Discharge silencing chamber) The refrigerant gas compressed inside the first and second cylinders 16 and 17 is discharged through discharge ports formed in the main bearing 23 and the sub-bearing 24, respectively, into discharge silencing chambers 28 and 29 formed on the side of the main bearing 23 facing the electric element 4 and on the side of the sub-bearing 24 facing the electric element 4.

[0040] The discharge silencing chamber 28 on the electric element 4 side is formed by attaching a discharge silencing plate 30, which has an opening centered on the part through which the rotating shaft 5 of the main bearing 23 passes, to the main bearing 23 by covering the area around the bearing part. The high-pressure side of the first cylinder 16 communicates with the main bearing 23 through an opening in the discharge silencing chamber 28.

[0041] Furthermore, the discharge silencing chamber 29 on the oil pump 13 side is formed by attaching the cup-shaped discharge silencing plate 31 to the sub-bearing 24, including the bearing portion of the sub-bearing 24, from the oil pump 13 side. As shown in the diagram, a mounting hole is provided in the center of the discharge silencer plate 31, to which the oil suction pipe 15 of the oil pump 13 is attached. The high-pressure side of the second cylinder 17 is connected to the sub-bearing 24 through an opening in the discharge silencer chamber 29.

[0042] The discharge silencer chamber 28 and the discharge silencer chamber 29 are connected by a passage (not shown) that penetrates the first and second cylinders 16 and 17 (plate portions of the cylinders) and the intermediate partition plate 18, reaching into the discharge silencer chamber 28 and opening up. In Figure 1, reference numeral 32 denotes a through hole formed in the cylinder-corresponding portion of the main bearing 23, which is the end of the passage on the discharge silencer chamber 28 side.

[0043] When the rotating compression element 8 is operating, the high-pressure refrigerant gas compressed by the second rotating compression element 7 is discharged into the discharge silencing chamber 28 via the discharge silencing chamber 29 and the aforementioned connecting passage. In addition, the high-pressure refrigerant gas compressed by the first rotating compression element 6 is discharged into the discharge silencing chamber 28, merges with the high-pressure refrigerant gas compressed by the second rotating compression element 7, and is discharged towards the electric element 4 through the opening that penetrates the bearing portion of the main bearing 23 of the discharge silencing plate 30 and the bearing portion itself. For the sake of clarity, Figure 1 depicts the through-hole at the end of the connecting passage on the discharge sound-dampening chamber 28 side and the space inside the first cylinder 16 facing each other.

[0044] At this time, the refrigerant gas h contains oil f supplied to the first and second rotating compression elements 6 and 7, and this oil f is also discharged to the electric element 4 side inside the sealed container 2. Here, the oil f mixed in with the refrigerant gas h then separates from the refrigerant gas h and accumulates in the oil reservoir 3 at the bottom of the sealed container 2. In this way, the space above the oil reservoir 3 inside the sealed container 2 becomes an oil separation space.

[0045] (Axis of rotation) The rotating shaft 5 is provided with an oil passage (not shown) extending from the end of the rotating shaft 5, which is supported by the sub-bearing 24, towards the electric element 4, on the rotational centerline. The oil pump 13 has a known configuration that guides oil toward the electric element 4 at the end of the oil passage supported by the sub-bearing 24, and also draws oil from the oil suction pipe 15.

[0046] Furthermore, the rotating shaft 5 is provided with small holes for guiding oil into the bearing portions of the first rotating compression element 6 and the second rotating compression element 7, as well as the main bearing 23 and the sub-bearing 24, and these small holes are in communication with the oil passage. Oil is supplied to the first rotating compression element 6 and the second rotating compression element 7, as well as the bearing portions of the main bearing 23 and the sub-bearing 24, through the oil passage of the rotating shaft 5 and the small holes, thereby providing lubrication.

[0047] Therefore, as described above, the refrigerant gas h is mixed with the oil f supplied to the first and second rotary compression elements 6 and 7, and the fluid consisting of the refrigerant gas h containing the oil f is discharged to the electric element 4 side in the sealed container 2. In the horizontal rotary compressor 1, the oil is separated from the fluid discharged to the electric element 4 side, the separated oil f is collected in the oil reservoir 3, and the fluid that has undergone oil separation, i.e., the compressed refrigerant gas h, is discharged to the outside of the sealed container 2.

[0048] (Pressure control plate) Furthermore, the horizontal rotary compressor 1 of this embodiment creates a differential pressure when oil separation is performed, increasing the pressure in the space on the electric element 4 side of the sealed container 2 and decreasing the pressure in the space on the oil pump 13 side. This raises the height of the oil level 49 in the oil reservoir 3 on the oil pump 13 side, ensuring that the oil pump 13 properly draws up oil. In addition, the oil separation is performed efficiently so that the refrigerant gas is discharged outside the sealed container 2.

[0049] In order to create the differential pressure described above when performing oil separation, the horizontal rotary compressor 1 is equipped with pressure control plates on the electric element 4 side of the rotary compression element 8 and on the oil pump 13 side.

[0050] (First pressure control plate) In this embodiment, the first pressure control plate 33 is positioned on the electric element 4 side of the first rotary compression element 6. The first pressure control plate 33 is formed along the outer circumference of the discharge silencing chamber 28 and is made of an annular steel plate as shown in Figure 4. The central opening portion into which the discharge silencing plate 30 forming the discharge silencing chamber 28 is fitted has two mounting pieces 34 that protrude toward the center of the opening, and these mounting pieces 34 are superimposed on the discharge silencing plate 30 and fastened together with the discharge silencing plate 30 to the main bearing 23 with screws.

[0051] Furthermore, the discharge sound-absorbing plate 30 is made of the same type of steel as the first pressure control plate 33.

[0052] The outer edge 35 of the annular first pressure control plate 33 is circular in shape around almost its entire circumference, as shown in Figure 4. In Figures 3(c) and 4(a), a portion of the outer edge is made straight to avoid interference with other parts during compressor assembly. This portion with a straight edge is included in the part that is submerged in the oil of the oil reservoir 3.

[0053] The discharge sound-dampening plate 30 and the first pressure control plate 33 are attached from the electric element 4 side of the main bearing 23, and the outer edge 35 of the first pressure control plate 33 is in close proximity to the inner circumferential surface 42 of the sealed container 2 with a gap in between.

[0054] Since the circular outer edge 35 of the first pressure control plate 33 is close to the inner circumferential surface 42 of the sealed container 2 with a gap in between, the first pressure control plate 33, when positioned on the side of the rotary compression element 8 that faces the electric element 4, partially divides the upper part of the sealed container 2 into the electric element 4 side and the rotary compression element 8 side. The undivided portion is the space between the outer edge 35 of the first pressure control plate 33 and the inner circumferential surface 42 of the sealed container 2.

[0055] Furthermore, the space between the outer edge 35 of the unpartitioned first pressure control plate 33 and the inner circumferential surface 42 of the sealed container 2 becomes a portion through which a fluid consisting of a refrigerant gas containing oil can pass from the electric element 4 side to the rotary compression element 8 side. Thus, in the horizontal rotary compressor 1 of this embodiment, the first pressure control plate 33 partially partitions the upper part of the sealed container 2 into the electric element 4 side and the rotary compression element 8 side, and forms a substantially annular first fluid passage portion 39 consisting of the gap along the outer edge 35 of the first pressure control plate 33.

[0056] The roughly annular first fluid passage section 39 is formed at a sufficient distance so that a slight differential pressure is created between the electric element 4 side and the rotary compression element 8 side when a fluid consisting of a refrigerant gas h containing oil f passes through it.

[0057] The refrigerant gas h (fluid including oil f), which is compressed by the first and second rotating compression elements 6 and 7 and discharged from the discharge silencer chamber 28 towards the space where the electric element 4 is located, passes through the first fluid passage section 39, creating a slight differential pressure as described above. However, the fluid that has passed through the space on the electric element 4 side flows unimpeded towards the rotating compression element 8 side.

[0058] (Second pressure control plate) As shown in Figure 2, the horizontal rotary compressor 1 described above has a refrigerant discharge pipe 40 provided on the side of the container 2, extending from the top of the container 2 in the direction of the container's circumference. Furthermore, as mentioned above, the horizontal rotary compressor 1 also has a pressure control plate on the oil pump 13 side of the rotating compression element 8.

[0059] As shown in Figure 2, a pressure control plate is provided as a second pressure control plate 41 located on a portion of the outer circumference of the discharge sound-dampening chamber 29, on the oil pump 13 side of the rotating compression element 8, at a position in the circumferential direction of the sealed container 2 that does not substantially overlap with the refrigerant discharge pipe 40.

[0060] As shown in Figure 5, the second pressure control plate 41 is formed from a steel plate integrated with the discharge sound-dampening plate 31 that forms the discharge sound-dampening chamber 29. This second pressure control plate 41 has a roughly arc shape and extends from the second rotating compression element 7 side toward the sealed container 2, with its outer edge 43 on the sealed container 2 side being close to the inner circumferential surface 42 of the sealed container 2 via a gap.

[0061] Since the outer edge 43 of the second pressure control plate 41 facing the inner circumferential surface 42 of the sealed container 2 is close to the sealed container 2 with a gap in between, the second pressure control plate 41, when positioned on the side of the rotating compression element 8 that faces the oil pump 13, partially partitions the upper part of the sealed container 2 into the side facing the rotating compression element 8 and the side facing the oil pump 13. The unpartitioned areas are the space between the outer edge 43 of the second pressure control plate 41 and the inner circumferential surface 42 of the sealed container 2, and the area around the body passing through the second pressure control plate 41 where the second pressure control plate 41 itself does not exist.

[0062] The discharge sound-dampening plate 31, which is integrated with the second pressure control plate 41, does not have any protruding portion on the lower side of the sealed container 2 that would impede the movement of oil, and the lower part of the discharge sound-dampening plate 31 is directly submerged in the oil f of the oil reservoir 3.

[0063] The space between the outer edge 43 of the second pressure control plate 41, which is not partitioned, and the inner circumferential surface 42 of the sealed container 2 is a portion through which a fluid consisting of refrigerant gas h containing oil f can pass from the space on the rotating compression element 8 side toward the space on the oil pump 13 side.

[0064] Therefore, in the horizontal rotary compressor 1 of this embodiment, the second pressure control plate 41 partially divides the upper part of the sealed container 2 into the side with the rotating compression element 8 and the side with the oil pump 13, and a substantially arc-shaped second fluid passage portion 44 consisting of a gap is formed along the outer edge 43 of the second pressure control plate 41.

[0065] (refrigerant discharge pipe) As described above, the refrigerant discharge pipe 40 is located in a portion of the sealed container 2 that is offset from the top of the container in the direction of the container's circumference towards the side of the container (Figure 2). Furthermore, the lower end of this refrigerant discharge pipe 40 differs from that of the conventional horizontal rotary compressor a shown in Figure 10. In this embodiment, the refrigerant discharge pipe 40 extends into the interior of the sealed container 2 and has an extension pipe portion 46 that extends from the position of the body wall 45 of the sealed container 2 toward the end opposite to the terminal 10 in the longitudinal direction of the sealed container 2.

[0066] The portion of the refrigerant discharge pipe 40 located on the outside of the sealed container 2 has a curved section, similar to conventional designs, through which it connects to equipment not shown. It also proceeds into the interior of the sealed container 2 perpendicular to the body wall 45 of the sealed container 2. The extension pipe section 46 extends towards the end of the sealed container 2 (the end opposite to the terminal 10) through a curved section, and the straight pipe section 47 is inclined diagonally downward. Therefore, the entire refrigerant discharge pipe 40 has a roughly S-shape when viewed from the side in the state where it is attached to the sealed container 2, as shown in Figure 7.

[0067] The straight pipe section 47 of the extension pipe section 46 is provided with eight through-holes 48 that penetrate and open in a direction along the circumference of the sealed container 2, and are arranged in a symmetrical pattern of four holes each with respect to the central axis of the pipe.

[0068] Figure 2 schematically shows the flow of oil f and refrigerant gas h in the space on the oil pump 13 side of the sealed container 2 (the space above the oil reservoir 3), where the oil f and refrigerant gas h flow in a direction along the circumference of the sealed container 2.

[0069] The extension pipe section 46 of the refrigerant discharge pipe 40 is positioned perpendicular to the flow of oil f and refrigerant gas h, with four through-holes 48 located on both the upstream side (where the mixed fluid hits the extension pipe section 46) and the downstream side (where the mixed fluid exits the extension pipe section 46). In this extension pipe section 46, as the refrigerant gas h containing oil f passes through the through-holes 48, it is separated into oil f and refrigerant gas h. The refrigerant gas h is discharged outside the sealed container 2 through the inside of the extension pipe section 46, while the oil f accumulates at the lower end of the extension pipe section 46 and overflows from the through-holes 48 into the oil reservoir 3.

[0070] In this way, when the refrigerant gas h is sent out of the sealed container 2 from the space of the oil pump 13 through the refrigerant discharge pipe 40, the oil f and refrigerant gas h are separated in the extension pipe section 46, thus reducing the amount of oil discharged to the outside of the sealed container 2.

[0071] Figure 7 shows the refrigerant discharge pipe 40 alone. In this embodiment, the extension pipe section 46 is gently bent at a bending angle 50 of 110° from the position of the body wall 45. It is shown that the straight pipe section 47 that slopes downwards continuously from the bent pipe section has four through holes 48 opening on both the upstream side and the downstream side in the direction of refrigerant gas flow. Furthermore, the through-holes 48 have a diameter of 3 mm and are arranged along the length of the straight pipe section 47 at a pitch 51 of 10 mm apart. Note that the end of the straight pipe section 47 is closed.

[0072] By providing eight through-holes 48 with a diameter of 3 mm, in sets of four, the total cross-sectional area of ​​all the through-holes 48 (the sum of the areas of the through-holes 48) becomes more relative to the longitudinal cross-sectional area inside the refrigerant discharge pipe m in the conventional example. In other words, in this embodiment, the pipe material of the refrigerant discharge pipe 40 and the pipe material of the refrigerant discharge pipe m in the conventional example are the same pipe material and have the same inner diameter. Therefore, as shown in Table 1 below, in the refrigerant discharge pipe 40 equipped with eight through holes 48 with a diameter of 3 mm, the ratio of the total cross-sectional area of ​​the through holes 48 to the cross-sectional area of ​​the inside of the pipe (the part that sends out the refrigerant gas) becomes large, so that the oil f and the refrigerant gas h can be separated efficiently, which is good.

[0073] (Consideration of the number of perforations in the refrigerant discharge pipe) Regarding the refrigerant discharge pipe 40, which has an expanded space on the oil pump 13 side of the sealed container 2 and an extension pipe section 46 provided toward the expanded space as described above, eight through holes 48 with a hole diameter of 3 mm were provided in the above embodiment. Based on refrigerant discharge pipes made as various samples using the current pipe material, the optimal range for these through holes 48 was examined, and the results are shown in Table 1 below.

[0074] In the conventional example, the hole at the lower end of the L-shaped refrigerant discharge pipe m corresponds to the through-hole 48 provided in the refrigerant discharge pipe 40 in this embodiment. The area of ​​the hole at the lower end opening in the conventional example is the cross-sectional area inside the pipe, and for samples made using the same pipe material as the conventional example, it was determined that it is desirable for the ratio of the total area of ​​the through-hole 48 to the cross-sectional area of ​​the hole in the conventional example (which is the same as the cross-sectional area inside the pipe of each sample) to be larger.

[0075] [Table 1]

[0076] Sample number 16 is a conventional L-shaped refrigerant discharge pipe m. ○In the conventional example, sample number 16, the refrigerant discharge pipe m has an open end located in the mounting hole of the body wall 45 of the sealed container 2, and the lower end of the refrigerant discharge pipe m is open and faces into the sealed container 2. ○In the conventional example, sample number 16, the refrigerant discharge pipe m has an opening at its lower end, and the part that acts as a through-hole is one of the openings at the lower end. ○In the conventional example, sample number 16, the hole diameter of 6.34 mm in the refrigerant discharge pipe m is the inner diameter of the pipe, and the cross-sectional area is 31.56955 mm². 2 This represents the area of ​​the cross-section inside the pipe. ○In the table, "Cross-sectional area" is the sum of the areas of all open pores in each sample. ○In the table, "percentage" is the ratio of the sum of the opening areas of the perforations in each sample to the cross-sectional area of ​​the lower end opening of the refrigerant discharge pipe in the conventional example described above, i.e., the cross-sectional area inside the pipe.

[0077] As shown in sample number 12, which is marked with a circle in Table 1, the refrigerant discharge pipe 40 is equipped with eight through-holes 48, each with a diameter of 3 mm, so that the total cross-sectional area of ​​these through-holes 48 is 179.1% of the internal cross-sectional area of ​​the pipe member. This indicates that the refrigerant gas h is discharged while separating a greater amount of oil f from the refrigerant gas h.

[0078] (Expansion of the oil reservoir) As shown in Figure 1, in this embodiment, the end of the sealed container 2 that faces the rotating compression element 8 is extended in a direction along the length of the sealed container 2. In this embodiment, the amount of extension is 40 mm compared to the sealed container of a conventional model. Therefore, the space on the rotating compression element 8 side inside the sealed container 2 is enlarged so that the length of the extension pipe portion 46 of the refrigerant discharge pipe 40 can be easily secured.

[0079] Furthermore, since the aforementioned end of the sealed container 2 is extended in a direction along the length of the sealed container 2, the bottom of the sealed container 2 widens in the direction of extension, and the space of the oil reservoir 3 on the oil pump 13 side is also expanded on the side opposite to the electric element 4 side of the rotating compression element 8. If the horizontal rotary compressor 1 of this embodiment were to be an inverter type, there is a possibility that the differential pressure would rise sharply at high rotational speeds. However, since the space of the oil reservoir 3 on the oil pump 13 side is enlarged (the oil storage capacity of the oil reservoir 3 on the oil pump 13 side is increased), the rise in the oil level 49 of the oil reservoir 3 on the oil pump 13 side is suppressed.

[0080] By suppressing the rise in the oil level 49 of the oil reservoir 3 and maintaining a wide space above the oil reservoir 3, it becomes more difficult for the refrigerant gas h containing oil f to be sent into the refrigerant discharge pipe 40, thereby reducing the amount of oil f discharged outside the sealed container 2.

[0081] Furthermore, since the oil level 49 in the oil reservoir 3 on the oil pump 13 side does not rise rapidly, more oil f than necessary is not sent to the rotating shaft 5 of the rotating compression element 8 and then moves into the space on the electric element 4 side. As a result, refrigerant gas h containing an excess amount of oil f does not return from the space on the electric element 4 side to the space on the oil pump 13 side. Therefore, from this point of view as well, it becomes more difficult for the refrigerant gas h containing oil f to be sent into the refrigerant discharge pipe 40, and the amount of oil f discharged outside the sealed container 2 can be reduced.

[0082] (Location of the second fluid passage) The aforementioned roughly arc-shaped second fluid passage section 44 consists of the gap between the outer edge 43 of the second pressure control plate 41 and the inner circumferential surface 42 of the sealed container 2. This roughly arc-shaped second fluid passage section 44 may be formed with a sufficient gap so that a small differential pressure is created between the rotating compression element 8 side and the oil pump 13 side when a fluid consisting of refrigerant gas h containing oil f passes through it.

[0083] The refrigerant gas h, compressed by the first and second rotating compression elements 6 and 7 and discharged through the space on the electric element 4 side and the first fluid passage section 39 to the space on the upper side of the rotating compression element 8, is then discharged through the second fluid passage section 44 to the space on the oil pump 13 side, thereby creating a small differential pressure. Of course, the fluid consisting of refrigerant gas h containing oil f flows without resistance into the space on the oil pump 13 side even when passing through this second fluid passage section 44.

[0084] Furthermore, as the refrigerant gas h containing oil f passes through the second fluid passage section 44, oil separation is efficiently performed, and the oil-separated refrigerant gas h moves toward the part to which the refrigerant discharge pipe 40 is attached. Since the second fluid passage section 44 is positioned close to the line through which the refrigerant discharge pipe 40 passes in the longitudinal direction of the sealed container 2, the oil-separated refrigerant gas h can easily enter the refrigerant discharge pipe 40, and this oil-separated refrigerant gas h is discharged.

[0085] This ensures that the oil level on the oil pump 13 side is maintained and lubrication is reliable, while the electric element 4 can be cooled with oil f, which has good thermal conductivity. Therefore, the operating performance of the electric element 4 and the flowability of the refrigerant gas are improved, and the various compressor functions of refrigerant gas intake, compression, and discharge can be ensured.

[0086] Furthermore, the refrigerant gas h discharged into the sealed container 2 can easily reach the part where the refrigerant discharge pipe 40 is attached after passing through the first fluid passage section 39 and the second fluid passage section 44, effectively separating the oil f mixed in the refrigerant gas h and directing it towards the refrigerant discharge pipe 40, thereby significantly reducing the amount of oil discharged outside the sealed container 2 via the refrigerant discharge pipe 40.

[0087] (Correlation between "oil discharge volume" and "refrigerant circulation volume and discharge pipe cross-sectional area ratio") Regarding the discharge of oil from the horizontal rotary compressor 1 to the sealed container 2, when the circulation rate of refrigerant gas h (the amount of refrigerant gas passing through the horizontal rotary compressor per unit time) increases, if the total area of ​​the through-holes 48 in the refrigerant discharge pipe 40 (the sum of the opening areas of the holes) is small, the degree to which oil and refrigerant gas are separated in the refrigerant discharge pipe 40 decreases. Furthermore, it was confirmed that when the total area of ​​the through-holes 48 becomes even smaller, the degree to which oil and refrigerant gas are separated decreases, and the discharge of oil to the sealed container 2 increases.

[0088] Therefore, the amount of refrigerant gas passing through the horizontal rotary compressor per unit time was defined as the "refrigerant circulation rate," and the total area of ​​the through-holes 48 in the refrigerant discharge pipe 40 was defined as the "discharge pipe cross-sectional area." As shown in Figure 8, the correlation between the oil discharge rate and the ratio of the refrigerant circulation rate to the discharge pipe cross-sectional area was expressed on a graph from five good measured values ​​(A, B, C, D, E) obtained by relating the "oil discharge rate" and the "ratio of the refrigerant circulation rate to the discharge pipe cross-sectional area." The measured values ​​for the five measurement samples used to examine the correlation are shown in Table 2 below.

[0089] [Table 2]

[0090] If the value of the "refrigerant circulation volume to discharge pipe cross-sectional area ratio" exceeds 500, the amount of oil discharged from the horizontal rotary compressor increases, causing the oil level to drop. This drop in oil level reduces the capacity of the horizontal rotary compressor and affects its durability. In the horizontal rotary compressor according to the above embodiment of the present invention, it is preferable that the "ratio of refrigerant circulation volume to discharge pipe cross-sectional area" is within a range of 200 or more, with an upper limit of 500 or less.

[0091] (Correlation between "oil discharge volume" and "volume of oil separation space inside the case and refrigerant circulation volume ratio") Furthermore, regarding the discharge of oil from the horizontal rotary compressor 1 to the outside of the sealed container 2, it was confirmed that when the size of the space above the oil reservoir 3 inside the sealed container 2 (volume of the oil separation space inside the case) decreases, the degree of separation between oil f and refrigerant gas h decreases, and the amount of oil f discharged to the outside of the sealed container 2 increases.

[0092] Therefore, as shown in Figure 9, the correlation between the oil discharge rate and the ratio of the oil separation space volume and refrigerant circulation rate within the case was graphically represented from five good measured values ​​(F, G, H, I, J) obtained by relating the "oil discharge rate" and the "ratio of the oil separation space volume within the case to the refrigerant circulation rate". The measured values ​​for the five measurement samples used to examine the correlation are shown in Table 3 below.

[0093] [Table 3]

[0094] Based on the amount of oil discharged from the sealed container of the horizontal rotary compressor, it is preferable that the value of "ratio of oil separation space volume inside the case to refrigerant circulation volume" be 0.03 or higher in the embodiment of the present invention. Furthermore, if the value falls below this (0.03), the oil discharge volume will increase, leading to a drop in the oil level, which will reduce the capacity of the horizontal rotary compressor and affect its durability. [Explanation of Symbols]

[0095] 1…Horizontal rotary compressor 2… airtight container 3… Oil reservoir 4...Electric element 8... Rotational compression element 13… Oil pump 14… Oil 23... Main bearing 24... Sub-bearing 33…First pressure control plate 40...Refrigerant discharge pipe 41…Second pressure control plate 45...Wall 46…Extension pipe section 47…Straight tube section 48…through hole 49… Oil noodles

Claims

1. Inside a horizontally sealed container, Electric elements, A rotary compression element driven by the aforementioned electric element, The lubricating oil stored in the oil reservoir at the bottom of the sealed container, An oil pump is provided on the opposite side of the rotary compression element from the electric element, for supplying oil to the rotary compression element. The upper part of the sealed container is partially divided into an electric element side and a rotary compression element side by an annular pressure control plate positioned on the electric element side of the rotary compression element, and a substantially annular fluid passage section is formed along the outside of this pressure control plate, The refrigerant discharge pipe located at the upper part of the sealed container, which is on the oil pump side, It is equipped with, The refrigerant discharge pipe proceeds into the interior of the sealed container perpendicular to the body wall of the sealed container, and has an extension pipe section that extends linearly diagonally downward via a curved pipe section and has a closed end. The horizontal rotary compressor is characterized in that the extension pipe section has a plurality of through-holes that penetrate and open in a direction along the circumference of the sealed container.

2. The horizontal rotary compressor according to claim 1, wherein the end of the sealed container on the oil pump side is extended in the longitudinal direction of the sealed container, and the oil reservoir space on the oil pump side is expanded on the side opposite to the electric element side of the rotating compression element.

3. A horizontal rotary compressor according to claim 1 or 2, wherein the ratio of the amount of refrigerant gas circulating through a sealed container to the combined opening area of ​​the perforations in the refrigerant discharge pipe is 500 or less.

4. A horizontal rotary compressor according to claim 1 or 2, wherein the ratio of the volume of space above the oil reservoir in the sealed container to the amount of refrigerant gas circulating through the sealed container is 0.03 or more.

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