Horizontal Rotary Compressor

Abstract

To provide a horizontal type compact rotary compressor which efficiently separates refrigerant gas containing oil into the oil and the refrigerant gas in a hermetically closed container, and can supply the refrigerant gas in a high circulation amount.SOLUTION: A partition portion by an approximately arc-shaped second pressure control plate 41 protruding toward an inner peripheral surface side of a hermetically closed container 2 is shifted into a position passing through a position where a refrigerant discharge pipe 40 is arranged in a lengthwise direction of the hermetically closed container 2.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a horizontal rotary compressor in which refrigerant gas compressed by a rotary compression element in a sealed container is first discharged together with lubricating oil to the side of an electric element in the sealed container, and then discharged outside the sealed container.

[0002] Conventionally, in this type of horizontal rotary compressor, refrigerant gas is sucked into the low-pressure chamber of the cylinder through the suction port of the rotary compression element, compressed by the action of the rollers and vanes, and discharged from the high-pressure chamber of the cylinder through the discharge port and the discharge sound-absorbing chamber into a sealed container, and then flows into an external radiator or the like.

[0003] In addition, the bottom of the sealed container serves as an oil reservoir, and an oil pump (oil supply means) attached to the opposite side of the rotary compression element from the electric element draws up lubricating oil from the oil reservoir and supplies it 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 discharged into the sealed container together with the refrigerant gas.

[0005] In order to promote the separation of oil from the refrigerant gas, the refrigerant gas is discharged from the rotary compression element to the electric element side of the cylinder, and then rotated from the electric element side to the rotary compression element side within the sealed container. The refrigerant gas is discharged to the outside from a refrigerant discharge pipe provided in the upper part of the sealed container on the oil pump side.

[0006] As a result, oil accumulates not only on the oil pump side but also on the electric element side, so if the oil level in the oil pump drops, a problem occurs in which the oil cannot be sucked up smoothly.

[0007] In order to prevent the above-mentioned problem of oil accumulating at the same oil level on both the oil pump side and the electric element side, a method has been proposed to create a pressure difference so that the pressure of the refrigerant gas on the electric element side in the sealed container is higher and the pressure of the refrigerant gas on the oil pump side is lower.

[0008] This technology is disclosed in Patent Document 1. In Patent Document 1, in order to create a pressure difference between the electric element side and the oil pump side, an annular pressure control plate acting as a baffle is provided on the electric element side of the rotary compression element, and a substantially arc-shaped pressure control plate acting as a baffle is also provided on the oil pump side of the rotary compression element.

[0009] In Patent Document 1, the annular pressure control plate provided on the electric element side of the rotary compression element is configured to partially divide the upper part of the sealed container into the electric 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 sealed container, and the gap between the annular pressure control plate and the sealed container is configured to be a gap where a pressure difference is generated when a fluid, which is a refrigerant gas containing oil, passes from the electric element side to the rotary compression element side.

[0010] In addition, the substantially arc-shaped pressure control plate provided on the oil pump side of the rotary compression element partially divides the portion of the sealed container, which is partitioned by the annular pressure control plate and extends from the rotary compression element side to the end side of the sealed container, into the rotary compression element side and the oil pump side. Specifically, the outer edge of this pressure control plate on the sealed container side is close to the inner surface of the sealed container, and the gap between the substantially arc-shaped pressure control plate and the sealed container is a gap at which a pressure difference is generated when the fluid passes from the rotary compression element side to the oil pump side.

[0011] In this way, an annular pressure control plate is provided on the electric element side of the rotary compression element, and a generally arc-shaped pressure control plate is provided on the oil pump side. The fluid consisting of refrigerant gas containing oil passes sequentially through gaps along the outer edges of both pressure control plates, thereby increasing the pressure on the electric element side and decreasing the pressure on the oil pump side.

[0012] In the horizontal rotary compressor equipped with the pressure control plate, the refrigerant gas containing oil discharged from the rotary compression element to the electric element is also guided to above the electric element. The refrigerant gas guided to the top of the electric element passes through the gaps around the annular pressure control plate, and then through the openings on the sides of the approximately arc-shaped pressure control plate and the gap between the plate and the sealed container, and the oil and the refrigerant gas are separated as they pass through these gaps.

[0013] The oil that is separated and falls into the oil sump moves to the oil pump side at the bottom of the sealed container due to the pressure difference created between the electric element side and the oil pump side, and raises the oil level of the oil that accumulates on the oil pump side, allowing the oil pump to smoothly suck up the oil. The refrigerant gas is also discharged out of the sealed container from a refrigerant discharge pipe attached to the top of the sealed container on the oil pump side. [Prior art documents] [Patent documents]

[0014] [Patent Document 1] JP 2003-269356 A Summary of the Invention [Problem to be solved by the invention]

[0015] Conventional horizontal rotary compressors are often used for low temperature applications and the amount of refrigerant circulated is small. Therefore, the discharge of oil from the horizontal rotary compressor to the outside is not often considered a problem, and the oil discharged from the compressor can be dealt with by the refrigerant-using equipment.

[0016] In recent years, compressors used in air conditioning applications are required to supply a high amount of refrigerant gas in circulation. In addition, there is a demand for compact compressors to increase the amount of circulation by using DC inverters.

[0017] However, in conventional horizontal rotary compressors, the position of the refrigerant discharge pipe that is effective for separating the refrigerant gas and the oil, the shape and position of the pressure control plate, and the distance from the rotary compression element to the end of the sealed container on the oil pump side are not specified in order to efficiently separate the oil, and there are limitations to effectively separating the refrigerant gas and the oil in the limited space inside the compressor.

[0018] In view of the above circumstances, the present invention has an object to provide a horizontal rotary compressor that is compact and can supply refrigerant gas at a high circulation rate, by efficiently separating oil-containing refrigerant gas into oil and refrigerant gas within a sealed container. [Means for solving the problem]

[0019] (The invention of claim 1) The present invention has been made in consideration of the above problems, and provides a refrigerant compressor comprising: an electric element; a rotary compression element driven by the electric element; oil for lubrication stored in an oil reservoir at the inner bottom of the sealed 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, the refrigerant compressor comprising: a refrigerant discharge pipe provided at an upper portion of the sealed container on the side of the oil pump; The upper part of the sealed container is an annular first compression element disposed on the side of the rotary compression element on the electric element side. force a control plate that is partially partitioned into an upper portion on the electric element side and an upper portion on the rotary compression element side including an upper portion on the oil pump side, and forms a substantially annular first fluid passing portion along an outer side of the first pressure control plate; An upper portion of the sealed container on the side of the rotary compression element is provided with a void space between the rotary compression element and the inner circumferential surface of the sealed container, the void space being a portion where the rotary compression element is not present, A substantially arc-shaped second pressure control plate is disposed in the cavity provided in the upper portion of the sealed container on the side of the rotary compression element, In the second pressure control plate, an upper portion on the rotary compression element side in the sealed container is partially partitioned into an upper portion on the rotary compression element side and an upper portion on the oil pump side, forming an arc-shaped second fluid passing portion along the outer side of the second pressure control plate, The second pressure control plate is formed integrally with a cup-shaped discharge sound absorbing plate disposed closer to the oil pump than the rotary compression element, and is connected to a portion extending from the oil pump side to the electric element side via a bent portion and disposed in the cavity. The present invention provides a horizontal rotary compressor characterized by the above-mentioned, thereby solving the above problems.

[0020] (The invention of claim 2) In the present invention, the ratio (Dm / Dup) of the outer diameter (Dup) of the first pressure control plate to the outer diameter (Dm) of the first fluid passing portion is 1 <Dm / Dup<1.05 year, The ratio (Dc / Dlow) of the outer diameter (Dlow) of the ring along the outer edge of the second pressure control plate on the sealed container side to the inner diameter (Dc) of the sealed container, 1 <Dc / Dlow<1.05 year, 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 sealed container on the oil pump side is 3 <y / x<15 year, The ratio (d / x) of the distance (x) from the second pressure control plate to the center of the refrigerant discharge pipe to the inner diameter (d) of the refrigerant discharge pipe is 0.5 <d / x<3 year, It is preferable that the second pressure control plate is located upstream in the direction of fluid flow from a portion where the refrigerant discharge pipe is provided. Effect of the Invention

[0021] (Effect of the invention of claim 1) According to the invention of claim 1, As shown in Figure 1 Second pressure control plate and a portion where the refrigerant discharge pipe is attached to the sealed container.Along the length of the sealed container The arrangement is such that they are lined up in a staggered manner. The refrigerant gas that has been separated from the oil by passing through the first fluid passing section and the second fluid passing section immediately reaches the refrigerant discharge pipe and enters this refrigerant discharge pipe, thereby providing the excellent effect of efficiently reducing the proportion of oil contained in the refrigerant gas discharged outside the sealed container.

[0022] (Effect of the invention of claim 2) According to the invention of claim 2, there is an excellent effect that the ratio of oil contained in the refrigerant gas discharged to the outside of the sealed container can be reduced extremely efficiently. [Brief description of the drawings]

[0023] [Figure 1] FIG. 3 is an explanatory diagram illustrating the movement of oil and refrigerant gas in the horizontal rotary compressor according to the embodiment of the present invention, taken at a radial cross section taken along line aa in FIG. 2. [Diagram 2] FIG. 2 is an explanatory diagram showing the embodiment as viewed from the oil pump side. [Diagram 3] 1A is an explanatory diagram showing a rotary compression element, where (a) is an explanatory diagram showing the second pressure control plate as viewed from the oil suction pipe side, (b) is an explanatory diagram showing the rotary compression element as viewed from a direction intersecting the rotational axis direction, and (c) is an explanatory diagram showing the first pressure control plate as viewed from the front. [Figure 4] 1A and 1B show a first pressure control plate, where FIG. 1A is an explanatory view showing the state as seen from one side, and FIG. [Diagram 5] 1A shows a second pressure control plate and a discharge sound absorbing plate, where (a) is an explanatory diagram showing the state as seen from one side, and (b) is an explanatory diagram showing a cross section along line aa in (a). FIG. [Figure 6] 3 is an explanatory diagram showing an enlarged view of a part of a radial cross section taken along line aa in FIG. 2; FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0024] Next, the present invention will be described in detail based on an embodiment. In the figure, 1 is a horizontal rotary compressor, and as shown in FIG. 1, the horizontal rotary compressor 1 is provided with a horizontally elongated cylindrical sealed container 2 with both ends sealed, and the inner bottom of the sealed container 2 serves as an oil reservoir. Inside the sealed container 2, an electric element 3 and a rotary compression element (rotary compression mechanism) 7 consisting of a first rotary compression element 5 and a second rotary compression element 6 driven by a rotary shaft 4 of the electric element 3 are housed. Note that FIG. 1 shows a schematic configuration of the embodiment at a cross section taken along line aa in FIG. 2, and for ease of explanation, the cross section is partially changed as shown in FIG. 2.

[0025] (Electric element) A circular mounting hole 8 is formed in the end of the sealed container 2 on the side of the electric element 3. A terminal 9 for supplying electric power to the electric element 3 is attached to the mounting hole 8.

[0026] The electric element 3 is composed of a stator 10 attached in an annular shape along the inner peripheral surface of the sealed container 2, and a rotor 11 rotatably inserted inside the stator 10 with a small gap provided. The rotor 11 is fixed to a rotating shaft 4 that passes through the center of the rotor 11 and extends in the longitudinal direction of the sealed container 2.

[0027] The stator 10 has a laminate of donut-shaped electromagnetic steel sheets and a stator coil wound around the teeth of the laminate by a direct winding (concentrated winding) method. The rotor 11 is also formed of a laminate of electromagnetic steel sheets, just like the stator 10.

[0028] (Oil pump) An oil pump 13, which serves as an oil supply means, is formed on the side of the rotary compression element 7 consisting of the first rotary compression element 5 and the second rotary compression element 6 opposite the electric element 3, i.e., on the end of the rotary compression element 7 side of the rotating shaft 4.

[0029] The oil pump 13 is provided to suck up lubricating oil 14 from an oil reservoir formed using the inner bottom of the sealed container 2, and supply it to each sliding portion of the first rotary compression element 5 and the second rotary compression element 6 in the rotary compression element 7 to prevent 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 opens in the oil reservoir.

[0030] (Rotary compression element) The first rotary compression element 5 has a first cylinder 16, and the second rotary compression element 6 has a second cylinder 17. An intermediate partition plate 18 is positioned 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) 7 includes the first rotary compression element 5, the second rotary compression element 6, and the intermediate partition plate 18.

[0031] The first and second rotary compression elements 5, 6 are respectively composed of first and second cylinders 16, 17 arranged on both sides (left and right in FIG. 1 ) of an intermediate partition plate 18, first and second rollers 21, 22 fitted into first and second eccentric portions 19, 20 provided on the rotating shaft 4 with a phase difference of 180 degrees and eccentrically rotating within the first and second cylinders 16, 17, vanes (not shown) abutting against these rollers 21, 22, respectively, to divide the insides of the first and second cylinders 16, 17 into a low pressure chamber side and a high pressure chamber side, and a main bearing 23 and an auxiliary bearing 24 that also serve as bearings for the rotating shaft 4 by respectively closing an opening face of the first cylinder 16 on the electric element 3 side and an opening face of the second cylinder 17 on the opposite side to the electric element 3 (the oil pump 13 side).

[0032] A suction passage 25 is formed in the first cylinder 16, which communicates with the low pressure chamber inside the first cylinder 16 at a suction port. A suction passage 26 is also formed in the second cylinder 17 and the intermediate partition plate 18, which communicates with the low pressure chamber inside the second cylinder 17 at a suction port.

[0033] These suction passages 25, 26 are connected to one end of a refrigerant introduction pipe 27 described later, and refrigerant gas is supplied from the refrigerant introduction pipe 27 through the respective suction passages 25, 26 and suction ports to the first and second cylinders 16, 17.

[0034] (Discharge silencing chamber) The refrigerant gas compressed inside the first and second cylinders 16, 17 is discharged through discharge ports formed in the main bearing 23 and the sub bearing 24, respectively, into discharge sound-absorbing chambers 28, 29 formed on the electric element 3 side of the main bearing 23 and the opposite side of the electric element 3 of the sub bearing 24.

[0035] The discharge sound-reducing chamber 28 on the electric element 3 side is formed by attaching a discharge sound-reducing plate 30, which has an opening centered on the portion through which the bearing portion of the main bearing 23 for the rotating shaft 4 penetrates, to the main bearing 23 so as to cover the periphery of the bearing portion. In the discharge sound-reducing chamber 28, the high pressure side of the first cylinder 16 communicates with the main bearing 23 via a through hole at the opening.

[0036] Further, the discharge sound-absorbing chamber 29 on the oil pump 13 side is formed by attaching a cup-shaped discharge sound-absorbing plate 31 to the sub-bearing 24, including the bearing portion of the sub-bearing 24, so as to cover the sub-bearing 24 from the oil pump 13 side. As shown in the figure, a mounting hole is provided in the center of the discharge sound-absorbing plate 31, to which the oil suction pipe 15 of the oil pump 13 is attached. In the discharge sound-absorbing chamber 29, the high pressure side of the second cylinder 17 communicates with the sub-bearing 24 via an opening through hole.

[0037] The discharge silencing chamber 28 and the discharge silencing chamber 29 are in communication with each other through a communication passage (not shown) that penetrates the first and second cylinders 16, 17 (the plate material portions of the cylinders) and the intermediate partition plate 18, reaching and opening into the discharge silencing chamber 28. In Fig. 6, reference numeral 32 denotes the end of the communication passage on the discharge silencing chamber 28 side, and is a through hole formed in the portion of the main bearing 23 corresponding to the cylinder.

[0038] When the rotary compression element 7 is operating, high-pressure refrigerant gas compressed by the second rotary compression element 6 is discharged to the discharge silencing chamber 28 through the discharge silencing chamber 29 and the above-mentioned communication passage. In addition, high-pressure refrigerant gas compressed by the first rotary compression element 5 is discharged to the discharge silencing chamber 28, merges with high-pressure refrigerant gas compressed by the second rotary compression element 6, and is discharged to the electric element 3 side through an opening portion through which the bearing portion of the main bearing 23 of the discharge silencing plate 30 penetrates and between that bearing portion.

[0039] At this time, the oil supplied to the first and second rotary compression elements 5 and 6 is mixed in the refrigerant gas, and this oil is also discharged to the electric element 3 side in the sealed container 2. Here, the oil mixed in the refrigerant gas is subsequently separated from the refrigerant gas and collected in an oil reservoir at the inner bottom of the sealed container 2.

[0040] (rotation axis) An oil passage (not shown) is provided on the rotating shaft 4 from the end side of the rotating shaft 4 supported by the sub-bearing 24 on the rotation center line toward the electric element 3. The oil pump 13 has a known configuration for directing oil toward the electric element 3 at the end side of the oil passage supported by the sub-bearing 24 and for sucking oil from the oil suction pipe 15 side.

[0041] Furthermore, the rotating shaft 4 is provided with small holes for guiding oil to the first rotary compression element 5, the second rotary compression element 6, and the bearing parts of the main bearing 23 and the sub-bearing 24, and these small holes are connected to the oil passage. Oil is supplied to the first rotary compression element 5, the second rotary compression element 6, and the bearing parts of the main bearing 23 and the sub-bearing 24 via the oil passage of the rotating shaft 4 and the small holes, thereby providing lubrication.

[0042] 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 a fluid composed of the refrigerant gas containing oil is discharged to the side of the electric element 3 in the sealed container 2. In the horizontal rotary compressor 1, oil separation is performed from the fluid discharged to the side of the electric element 3, and the separated oil collects in the oil reservoir. Also, the fluid that has undergone oil separation, that is, the compressed refrigerant gas, is discharged outside the sealed container 2.

[0043] (Pressure control plate) Furthermore, the horizontal rotary compressor 1 of the present embodiment forms a differential pressure when oil separation is performed, raises the pressure in the space on the electric element 3 side of the sealed container 2, and lowers the pressure in the space on the oil pump 13 side. As a result, the height of the oil level in the oil reservoir on the oil pump 13 side is increased, and the oil suction of the oil pump 13 is appropriately performed. Furthermore, oil separation is efficiently performed so that the refrigerant gas is discharged outside the sealed container 2.

[0044] In order to form the differential pressure when performing oil separation, the horizontal rotary compressor 1 is provided with pressure control plates on the electric element 3 side and the oil pump 13 side of the rotary compression element 7.

[0045] (First pressure control plate) In the present embodiment, a first pressure control plate 33 is disposed on the electric element 3 side of the first rotary compression element 5. The first pressure control plate 33 is formed along the outer periphery of the discharge silencing chamber 28 and is composed of a steel plate having an annular shape as shown in FIG. 4. And in the central opening portion into which the discharge silencing plate 30 forming the discharge silencing chamber 28 is fitted, it has two mounting pieces 34 projecting toward the center of this opening portion. This mounting piece 34 is overlapped with the discharge silencing plate 30 and is screwed to the main bearing 23 together with the discharge silencing plate 30.

[0046] Note that the discharge silencing plate 30 is made of the same type of steel material as the first pressure control plate 33.

[0047] The outer edge 35 of the annular first pressure control plate 33 is circular around almost the entire circumference, as shown in Fig. 4. In Fig. 3(c) and Fig. 4(a), a part of the outer edge is a straight edge for reasons such as avoiding interference with other parts when assembling the compressor. This straight edge part is included in the part that is submerged in oil in the oil sump.

[0048] The main bearing 23, to which the discharge sound-absorbing plate 30 and the first pressure control plate 33 are attached, includes a plate portion 36 that spreads radially around the bearing portion, and a flange 37 that is in close contact with the inner peripheral surface of the sealed container 2 and is continuous with the plate portion 36. As shown in Figures 1 and 6, in the portion having a substantially L-shaped cross section formed by the plate portion 36 and the flange 37 around the bearing portion of the main bearing 23, the flange 37 is extended from the outer periphery of the plate portion 36 toward the electric element 3.

[0049] The discharge silencer plate 30 and the first pressure control plate 33 are attached from the electric 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 surface of the flange 37 via a gap.

[0050] 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 first pressure control plate 33 is disposed on the motor element side of the rotary compression element 7, and the upper part of the sealed container 2 is As shown in Figure 1 Electric element 3 side Top and , including the upper part on the oil pump 13 side Rotary compression element 7 side Top The non-partitioned portion is between the outer edge 35 of the first pressure control plate 33 and the inner circumferential surface 38 of the flange 37.

[0051] The unpartitioned space between the outer edge 35 of the first pressure control plate 33 and the inner circumferential surface 38 of the flange 37 is a portion through which a fluid made of refrigerant gas containing oil can pass from the electric element 3 side toward the rotary compression element 7 side. Therefore, in the horizontal rotary compressor 1 of this embodiment, the first pressure control plate 33 is As shown in Figure 1 The upper part of the sealed container 2、 On the side of the electric element 3 Top and , including the upper part on the oil pump 13 side On the side of the rotary compression element 7 Top are partially partitioned, and a substantially annular first fluid passage portion 39 formed of the gap is formed along the outer edge 35 of the first pressure control plate 33.

[0052] The substantially annular first fluid passage portion 39 is formed at a sufficient interval such that a slight differential pressure is formed between the side of the electric element 3 and the side of the rotary compression element 7 when a fluid composed of a refrigerant gas containing oil passes therethrough.

[0053] A plurality of apertures having a sufficient area are provided in the plate portion 36 of the main bearing 23 so as not to hinder the movement of a fluid composed of a refrigerant gas containing oil and the movement of oil in the oil reservoir. Even when the refrigerant gas, which is a gas containing oil, passes through these holes, no differential pressure is formed at the aperture portion.

[0054] The refrigerant gas (fluid containing oil) compressed by the first and second rotary compression elements 5 and 6 and discharged from the discharge silencing chamber 28 to the space side where the electric element 3 is located passes through the first fluid passage portion 39, whereby a slight differential pressure is formed as described above. However, the fluid that has passed through the space on the side of the electric element 3 flows to the side of the rotary compression element 7 without support.

[0055] (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 at a portion on the side of the container side in the circumferential direction of the cylinder from the position of the top of the sealed container 2. And, as described above, the horizontal rotary compressor 1 is also provided with a pressure control plate on the side of the oil pump 13 of the rotary compression element 7, and this pressure control plate is As shown in FIG. 1, in the longitudinal direction of the sealed container 2, the refrigerant discharge pipe 40 is arranged in a shifted state toward the electric element 3 with respect to the portion attached to the sealed container 2. present.

[0056] In the present embodiment, on the side of the oil pump 13 of the rotary compression element 7, In the longitudinal direction of the sealed container 2, the refrigerant discharge pipe 40 is arranged in a shifted state toward the electric element 3 with respect to the portion attached to the sealed container 2. the pressure control plate is provided as a second pressure control plate 41 disposed on a part of the outer periphery of the discharge silencing chamber 29.

[0057] As shown in FIG. 5, the second pressure control plate 41 is formed of a steel plate integrated with the discharge silencing plate 31 that forms the discharge silencing chamber 29. This second pressure control plate 41 is omitted is formed in an arc shape and extends from the second rotary compression element 6 side toward the sealed container 2 can be , and the outer edge 43 on the sealed container 2 side is close to the inner peripheral surface 42 of the sealed container 2 with a gap therebetween.

[0058] Since the outer edge 43 of the second pressure control plate 41 facing the inner peripheral surface 42 side of the sealed container 2 is close to the sealed container 2 with a gap therebetween, the second pressure control plate 41 is arranged in a state where it is disposed on the portion on the oil pump 13 side of the rotary compression element 7, The upper part of the rotary compression element 7 including the upper part of the oil pump 13 and Furthermore is partially partitioned into Top the rotary compression element 7 side The top and and the oil pump 13 side. The non-partitioned portion is the portion 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 portion where the second pressure control plate 41 itself does not exist in the circumferential direction passing through the second pressure control plate 41.

[0059] On the lower side of the sealed container of the discharge silencing plate 31 itself integrated with the second pressure control plate 41, there is no portion protruding until it impairs the movement of oil, and the lower part of the discharge silencing plate 31 is directly immersed in the oil in the oil reservoir.

[0060] The space between the outer edge 43 of the second pressure control plate 41 that is not partitioned and the inner peripheral surface 42 of the sealed container 2 becomes a portion through which a fluid composed of a refrigerant gas containing oil can pass from the space on the rotary compression element 7 side to the space on the oil pump 13 side.

[0061] Therefore, in the horizontal rotary compressor 1 of the present embodiment, the second pressure control plate 41 The upper portion of the rotary compression element 7 including the upper portion of the oil pump 13 is further is partially partitioned into Top the rotary compression element 7 side Top and the oil pump 13 side, and a substantially arc-shaped second fluid passage portion 44 formed of a gap is formed in a portion along the outer edge 43 of the second pressure control plate 41.

[0062] (Position of second fluid passage portion) As described above, the second fluid passage portion 44 having a substantially arc shape is formed on the outer edge 43 of the second pressure control plate 41. Closely The gap is formed between the inner peripheral surface 42 of the closed container 2, and the partitioned portion by the second pressure control plate 41, i.e., the position of the second pressure control plate 41 itself, is As shown in FIG. 1, in the longitudinal direction of the sealed container 2, the refrigerant discharge pipe 40 is arranged in a shifted state toward the electric element 7 with respect to the portion attached to the sealed container 2. Therefore, the position of the second fluid passage portion 44 is also In the longitudinal direction of the sealed container 2, the refrigerant discharge pipe 40 is arranged in a shifted state toward the electric element 3 with respect to the portion attached to the sealed container 2. .

[0063] The substantially arc-shaped second fluid passage 44 is formed with a sufficient gap so that a slight pressure difference is created between the rotary compression element 7 side and the oil pump 13 side when a fluid consisting of refrigerant gas containing oil passes through.

[0064] The refrigerant gas compressed by the first and second rotary compression elements 5, 6 and discharged to the space on the electric element 3 side and to the space on the upper side of the rotary compression element 7 through the first fluid passing section 39 is discharged to the space on the oil pump 13 side through the second fluid passing section 44, thereby forming a slight pressure difference. Of course, the fluid flows freely into the space on the oil pump 13 side even when passing through the second fluid passing section 44.

[0065] The pressure difference created by the fluid passing through the second fluid passage 44 also increases the pressure in the space on the electric element 3 side of the sealed container 2, and decreases the pressure in the space on the oil pump 13 side. This increases the oil level in the oil reservoir on the oil pump 13 side, and contributes to ensuring that the oil pump 13 properly sucks up oil.

[0066] Furthermore, when the fluid passes through the second fluid passing portion 44, oil separation is efficiently performed, and the refrigerant gas separated from the oil moves toward the portion to which the refrigerant discharge pipe 40 is attached. Then, the second fluid passing portion 44 In the longitudinal direction of the sealed container 2, the refrigerant discharge pipe 40 is arranged in a shifted state toward the electric element 3 with respect to the portion attached to the sealed container 2. Therefore, the refrigerant gas separated from the oil easily enters the refrigerant discharge pipe 40, and this refrigerant gas separated from the oil is discharged.

[0067] Due to the pressure difference created by the fluid passing through the first fluid passage section 39 and the second fluid passage section 44, the oil stored in the oil reservoir at the bottom of the sealed container 2 moves to the oil pump 13 side, and the oil level on the oil pump 13 side rises. As a result, the opening at the end of the oil suction pipe 15 becomes immersed in the oil without hindrance, so that the oil pump 13 can smoothly supply oil to the sliding parts of the rotary compression element (rotary compression mechanism section) 7.

[0068] In addition, the first pressure control plate 33 and the second pressure control plate 41 create a pressure difference between the electric element 3 side and the oil pump 13 side, with the electric element 3 side being higher and the oil pump 13 side being lower, and this enables the oil that has accumulated on the electric element 3 side to move to the oil pump 13 side.

[0069] This ensures that the oil level on the oil pump 13 side is ensured to ensure oil supply, while the electric element 3 is cooled with oil having good thermal conductivity. This improves the operating performance of the electric element 3 and the flowability of the refrigerant gas, and ensures each performance as a compressor, namely, suction, compression, and discharge of the refrigerant gas.

[0070] In addition, the refrigerant gas discharged into the sealed container 2 easily reaches the portion where the refrigerant discharge pipe is attached after passing 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, thereby significantly reducing the amount of oil discharged outside the sealed container 2 through the refrigerant discharge pipe 40.

[0071] (Provision of Conditions) In the horizontal rotary compressor 1 of the embodiment, conditions such as the distance and position of each part are specified to enable more efficient separation of oil. The dimensional range of each part for specifying the conditions is shown in Fig. 6. Note that Fig. 6 shows a cross section of only a part of the horizontal rotary compressor 1 at a position along the cross-sectional line in Fig. 2.

[0072] 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 to the outer diameter (Dm) of the first fluid passing portion 39 is expressed as follows: 1 <Dm / Dup<1.05 It was decided.

[0073] Ratio (Dc / Dlow) Next, the ratio (Dc / Dlow) of the outer diameter (Dlow) of the ring along the outer edge 43 of the second pressure control plate 41 on the sealed vessel 2 side to the inner diameter (Dc) of the sealed vessel 2 is 1 <Dc / Dlow<1.05 It was decided. As described above, the outer edge 43 of the second pressure control plate 41 is arc-shaped, but this outer edge 43 is extended in the inner circumferential direction of the sealed container 2 to form a virtual ring. The outer diameter of the ring is defined as (Dlow).

[0074] 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 to the distance (y) from the second pressure control plate 41 to the inner end position of the oil supply means (oil pump 13) side of the sealed container 2 is calculated as follows: 3 <y / x<15 It was decided.

[0075] 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 to the inner diameter (d) of the refrigerant discharge pipe 40 is calculated as follows: 0.5 <d / x<3 It was decided.

[0076] As described above, the second pressure control plate 41 is located upstream in the fluid flow direction from the portion where the refrigerant discharge pipe 40 is provided.

[0077] In the above range, in the embodiment, Dm / Dup=1.03, Dc / Dlow=1.02, y / x=4.8, d / x=0.8 It was decided.

[0078] The amount of oil discharged from the refrigerant discharge pipe was compared using a horizontal rotary compressor of the embodiment under the above conditions and a horizontal rotary compressor of a conventional product, both of which were 1000 W.

[0079] (result) The oil discharge rate (mL / min) of the conventional horizontal rotary compressor was 7.6 / 25 at an operating frequency of 60 / 80 (rps), whereas the horizontal rotary compressor of this embodiment was 3.3 / 13.3 at the same operating frequency of 60 / 80 (rps).

[0080] From the above comparison, it was confirmed that in the horizontal rotary compressor 1 of the embodiment, the refrigerant gas and oil are separated within the sealed container 2, and the amount of oil discharged from the refrigerant discharge pipe 40 is reduced by approximately 60% compared to the conventional product. [Explanation of symbols]

[0081] 1. Horizontal rotary compressor 2. Airtight container 3…Electric element 4...Rotation axis 5…First rotary compression element 6…Second rotary compression element 7…Rotary compression element 13…Oil pump 14. Oil 15...Oil suction pipe 16...First cylinder 17...Second cylinder 23...Main bearing 24...Sub bearing 27...Refrigerant introduction pipe 30...Discharge sound deadening plate 31...Discharge sound deadening plate 33...First pressure control plate 35…Outer edge 36...Main bearing plate 37...Main bearing flange 38…Inner surface of flange 39...First fluid passage portion 40...Refrigerant discharge pipe 41...Second pressure control plate 42...Inner surface of sealed container 43...Outer edge of second pressure control plate 44...Second fluid passage portion

Claims

1. A horizontal sealed container is provided with an electric element, a rotary compression element driven by the electric element, oil for lubrication stored in an oil reservoir at the inner bottom of the sealed 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, and a refrigerant discharge pipe is provided at an upper part of the sealed container on the side of the oil pump, An upper portion of the sealed container is partitioned into an upper portion on the electric element side and an upper portion on the rotary compression element side including an upper portion on the oil pump side by an annular first pressure control plate disposed on a portion of the rotary compression element that is on the electric element side, and forms a substantially annular first fluid passing portion along the outer side of the first pressure control plate; An upper portion of the sealed container on the side of the rotary compression element is provided with a void space between the rotary compression element and the inner circumferential surface of the sealed container, the void space being a portion where the rotary compression element is not present, A substantially arc-shaped second pressure control plate is disposed in the cavity provided in the upper portion of the sealed container on the side of the rotary compression element, In the second pressure control plate, an upper portion on the rotary compression element side in the sealed container is partially partitioned into an upper portion on the rotary compression element side and an upper portion on the oil pump side, forming an arc-shaped second fluid passing portion along the outer side of the second pressure control plate, The second pressure control plate is formed integrally with a cup-shaped discharge sound absorbing plate disposed closer to the oil pump than the rotary compression element, and is connected to a portion extending from the oil pump side to the electric element side via a bent portion and disposed in the cavity. A horizontal rotary compressor characterized by the above.

2. The ratio (Dm / Dup) of the outer diameter (Dup) of the first pressure control plate to the outer diameter (Dm) of the first fluid passing portion, 1<Dm / Dup<1.05 year, The ratio (Dc / Dlow) of the outer diameter (Dlow) of the ring along the outer edge of the second pressure control plate on the sealed container side to the inner diameter (Dc) of the sealed container is 1<Dc / Dlow<1.05 year, The ratio (y / x) of the distance (x) from the second pressure control plate to the center of the refrigerant discharge pipe to the distance (y) from the second pressure control plate to the inner end position of the sealed container on the oil pump side is 3<y / x<15 year, The ratio (d / x) of the distance (x) from the second pressure control plate to the center of the refrigerant discharge pipe to the inner diameter (d) of the refrigerant discharge pipe is 0.5<d / x<3 year, 2. The horizontal rotary compressor according to claim 1, wherein the second pressure control plate is located upstream in a fluid flow direction from a portion where a refrigerant discharge pipe is provided.

Images