CN110056531B - Split floating ring, rotating shaft sealing device, compressor and air conditioner - Google Patents
Split floating ring, rotating shaft sealing device, compressor and air conditioner Download PDFInfo
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- CN110056531B CN110056531B CN201910355003.XA CN201910355003A CN110056531B CN 110056531 B CN110056531 B CN 110056531B CN 201910355003 A CN201910355003 A CN 201910355003A CN 110056531 B CN110056531 B CN 110056531B
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- 238000007667 floating Methods 0.000 title claims abstract description 119
- 238000007789 sealing Methods 0.000 title claims abstract description 50
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 230000001154 acute effect Effects 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 38
- 238000005299 abrasion Methods 0.000 abstract description 16
- 230000000694 effects Effects 0.000 description 12
- 230000009286 beneficial effect Effects 0.000 description 7
- 230000002349 favourable effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 241000446313 Lamella Species 0.000 description 3
- 230000009471 action Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000001125 extrusion Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000001737 promoting effect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 229910003460 diamond Inorganic materials 0.000 description 1
- 239000010432 diamond Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Sealing Devices (AREA)
Abstract
Split floating ring, pivot sealing device, compressor and air conditioner relate to the air conditioner field. The split floating ring comprises at least two ring petals, the ring petals are connected in series to form a ring body, the two adjacent ring petals are movably connected, a first annular dam, a second annular dam and an annular groove are arranged on the inner side wall of each ring petal, a concave area is arranged on the bottom wall of each annular groove, and the annular groove is formed between the first annular dam and the second annular dam along the axial direction of the ring body; the first annular dams enclose a first annular dam, the second annular dams enclose a second annular dam, and the annular grooves enclose an annular groove. On the one hand, after the rotating shaft is opened, the split floating ring can be opened quickly, so that friction between the split floating ring and the rotating shaft is reduced, and abrasion of the split floating ring is reduced; on the other hand, the concave area dampens the flow of the fluid, so that the resistance of the fluid passing through the annular groove is increased, the sealing performance of the split floating ring is improved, and the leakage of the fluid is reduced.
Description
Technical Field
The invention relates to the field of air conditioners, in particular to a split floating ring, a rotating shaft sealing device, a compressor and an air conditioner.
Background
The floating ring seal is a main means for preventing the shaft end of the rotary fluid machinery from leaking, and with the continuous expansion of the operation working conditions of industries such as petroleum and petrochemical industry, nuclear power generation, aerospace and the like, the floating ring seal is required to have higher stability, reliability and longer service life, and the leakage amount of the fluid is strictly controlled. The traditional floating ring seal has the advantages of stable dynamic performance, non-contact, low abrasion, high reliability, suitability for high speed and various pressure levels, wide working condition range and the like, and has been widely applied to shaft end sealing devices of centrifugal compressors and pump rotating shafts, in particular to centrifugal compressor sealing of dangerous process gases. However, the conventional floating ring seal needs to maintain a larger lubrication gap while reducing contact wear of the mating end surfaces, which increases fluid leakage and makes the sealing performance limited.
The split floating ring is arranged on the basis of the traditional floating ring seal, the split floating ring comprises at least two ring petals, each ring petal is connected in series to form a ring body, two adjacent ring petals are movably connected, each ring petal is sealed by the radial compensation function of a unique floating ring petal structure under the action of pretightening force, the surface is allowed to slightly contact and wear and keep small gap running, the fluid leakage is reduced, but the dynamic pressure of the floating ring petal is slow to open, the ring petals are rubbed with a rotating shaft for a long time, the surfaces of the rotating shaft and the split floating ring are extremely easy to scratch, and the sealing failure is caused.
In addition, after the floating ring dynamic pressure is opened, if the gap between the floating ring and the rotating shaft is too large, the sealing effect is easy to be weakened, and if the gap between the floating ring and the rotating shaft is too small, friction between the ring valve and the rotating shaft is easy to be caused, the ring valve is worn, and the sealing failure is caused.
Disclosure of Invention
It is an object of the present invention to provide a split floating ring that facilitates reduced wear and improved sealing performance.
In order to achieve the above purpose, the split floating ring provided by the invention comprises at least two ring segments, wherein each ring segment is connected in series to form a ring body, two adjacent ring segments are movably connected, a first annular dam, a second annular dam and an annular groove are arranged on the inner side wall of each ring segment, a concave area is arranged on the bottom wall of each annular groove, and the annular groove is formed between the first annular dam and the second annular dam along the axial direction of the ring body; the first annular dams enclose a first annular dam, the second annular dams enclose a second annular dam, and the annular grooves enclose an annular groove.
Therefore, through the structural design of the split floating ring, the split floating ring is sleeved on the rotating shaft when in use, and when the rotating shaft is opened, the rotating shaft is rubbed with the first annular dam and the second annular dam, so that gaps are formed between each annular flap and the rotating shaft in the radial direction, fluid on two sides of the split floating ring enters the annular groove, and when air flows pass through the concave, a dynamic pressure effect is generated, so that each annular flap is quickly separated from the rotating shaft, the split floating ring is quickly opened, friction between the split floating ring and the rotating shaft is reduced, abrasion of the split floating ring is reduced, and abrasion of the rotating shaft is reduced; in addition, the concave area dampens the flow of the fluid, so that the resistance of the fluid passing through the annular groove is increased, the sealing performance of the split floating ring is improved, and the leakage of the fluid is reduced; in addition, after the split floating ring is opened, due to the sealing effect of the annular groove and the concave area on the bottom wall of the annular groove, under the condition that equal sealing performance is required, the distance between the first annular dam and the rotating shaft in the technical scheme can be set to be larger than the distance between the inner wall of the floating ring and the rotating shaft in the prior art, so that abrasion of the split floating ring in the running state is reduced, and abrasion of the rotating shaft is reduced.
In a preferred scheme, an elastic pull ring is sleeved on the ring body along the circumferential direction, and each ring flap is extruded on the inner side of the elastic pull ring.
From the above, when the split floating ring is used, the ring petals are extruded towards the rotating shaft by the pretightening force, and the pretightening force is generated in a mode that the pressure springs are arranged to be abutted to the peripheral wall of each ring petal, and the pressure springs are adopted to extrude each ring petal towards the rotating shaft; elastic braces can be respectively arranged between every two adjacent ring petals, and the two adjacent pull rings are tightly closed by adopting the elastic braces between the adjacent ring petals, so that the ring petals are closed towards the rotating shaft; compared with the two modes, the elastic pull ring is simple in structure and convenient to install, when the split floating ring is sleeved on the static rotating shaft, each ring is held tightly on the rotating shaft under the action of the elastic tension spring, and when the rotating shaft rotates and the split floating ring is opened, acting force between the rotating shaft and the split floating ring and extrusion tension force of the elastic tension spring reach an equilibrium state.
The further scheme is that the outer peripheral wall of the ring body is provided with a mounting groove which surrounds the ring body for a circle, and the elastic pull ring is sleeved in the mounting groove.
From the above, the installation groove is favorable for the installation stability of the elastic pull ring.
In another preferred embodiment, the distance between the bottom wall of the annular groove and the inner wall of the first annular dam is 0.1 to 1 mm in the radial direction of the ring body, and/or the distance between the bottom wall of the annular groove and the inner wall of the second annular dam is 0.1 to 1 mm.
In a further preferred scheme, an inserting joint is arranged at one end of the ring valve along the circumferential direction of the ring body, and an inserting groove is arranged at the other end of the ring valve; in the two adjacent ring petals, the plug connector of one ring petal is inserted into the plug groove of the other ring petal, and the plug connector and the groove wall of the plug groove are in clearance fit in the radial direction of the ring body.
Therefore, on one hand, the connection between the ring petals is good, and on the other hand, the ring petals can relatively move in the circumferential direction so as to meet the movement of the ring petals along the radial direction approaching to and separating from the rotating shaft, and the radial dimension change of the split floating ring is realized.
The further scheme is that along the radial direction of the ring body, the inner side of the inserting groove is provided with an inner side joint, the outer side of the inserting groove is provided with an outer side joint, the inner side joint is provided with a notch penetrating to the inner side wall of the ring body, and the inserting joint is provided with a bulge protruding inwards; in two adjacent ring petals, the bulge of one ring petal is inserted into the notch on the inner side joint of the other ring petal, and the bulge covers the circumferential gap of the inner side joint of the two ring petals along the axial direction of the ring body.
From the above, because each ring lamella can relatively move along circumference, consequently adjacent ring lamella has the clearance in circumference, and the clearance that keeps away from the pivot part on the split floating ring can be through external entity shutoff, and the clearance that is close to the pivot part can not be through external entity shutoff, therefore can lead to the sealing performance of split floating ring to descend, consequently, set up the breach on the interior side joint, set up the arch on the bayonet joint, the protruding peripheral clearance that covers adjacent ring lamella inboard joint department, the clearance that is close to the pivot of split floating ring obtains shutoff like this, is favorable to promoting the sealing performance of split floating ring.
Yet another preferred embodiment is a number of ring lobes ranging from 3 to 5.
In a further preferred embodiment, the recess comprises 0.05 to 0.5 of the total area of the bottom wall of the annular groove.
Yet another preferred embodiment is that the depth of the recessed area is 0.1 to 1 mm.
In a further preferred embodiment, the recess is a slot, and the length direction of the slot is the direction of spiral around the ring body.
From the above, the side wall of the strip-shaped groove has guiding effect on the flow direction of fluid, when the rotating shaft rotates, the fluid leaks from the gap between the split floating ring and the rotating shaft, the leakage direction is from the high pressure side to the low pressure side along the axial direction of the ring body, the strip-shaped groove with the length direction being spiral around the ring body is arranged, the strip-shaped groove can guide the fluid in the annular groove to the high pressure side, the difficulty of the fluid passing through the annular groove is further increased, and the sealing performance of the split floating ring is improved.
In another preferred scheme, the concave area is provided with blind holes, the blind holes are provided with a plurality of rows, the interval direction of each row of blind holes is along the axial direction of the ring body, and the blind holes in the same row are distributed along the circumferential direction of the ring body.
Therefore, the concave areas are uniformly distributed on the bottom wall of the annular groove, and uniform stress between each annular flap and the rotating shaft is facilitated.
The blind holes are elliptical holes, and the major axis direction of the elliptical holes is the direction of spiral around the ring body.
From the above, similar to the bar groove, the side wall of the oval hole can guide the air flow to the high pressure side along the long axis direction, so that the difficulty of fluid passing through the annular groove is improved, and the sealing performance of the split floating ring is improved.
Further, the blind holes are round holes, and the ratio of the depth of the round holes to the aperture of the round holes is 0.1-5.
In a further preferred embodiment, the recess is an annular throttling groove extending along the circumferential direction of the ring body, and each annular throttling groove is distributed along the axial direction of the ring body.
The second object of the invention is to provide a rotary shaft sealing device which is beneficial to reducing the abrasion of the split floating ring and improving the sealing performance.
In order to achieve the above purpose, the rotating shaft sealing device provided by the invention comprises a rotating shaft and the split floating ring, wherein the split floating ring is sleeved on the rotating shaft.
Therefore, on one hand, after the rotating shaft is opened, the split floating ring can be opened quickly, friction between the split floating ring and the rotating shaft is reduced, and abrasion of the split floating ring is reduced; on the other hand, the concave area dampens the flow of the fluid, so that the resistance of the fluid passing through the annular groove is increased, the sealing performance of the split floating ring is improved, and the leakage of the fluid is reduced.
It is a further object of the present invention to provide a compressor that facilitates reduced split floating ring wear and improved sealing performance.
In order to achieve the above object, the present invention provides a compressor including the aforementioned rotary shaft sealing device.
From the above, due to the adoption of the rotating shaft sealing device, the split floating ring can be opened quickly, so that the abrasion between the split floating ring and the rotating shaft is reduced, and the sealing performance of the split floating ring is improved.
The fourth object of the invention is to provide an air conditioner which is favorable for reducing the abrasion of the split floating ring and improving the sealing performance.
In order to achieve the above object, the present invention provides an air conditioner including the aforementioned compressor.
From the above, owing to adopt foretell compressor, split floating ring can open fast, is favorable to reducing split floating ring and the wearing and tearing between the pivot, is favorable to promoting split floating ring's sealing performance.
Drawings
FIG. 1 is a block diagram of a split floating ring embodiment of the present invention mounted on a rotating shaft;
FIG. 2 is an enlarged view of a portion of FIG. 1 at A;
FIG. 3 is a block diagram of an intermediate ring in accordance with one embodiment of the split floating ring of the present invention;
FIG. 4 is an enlarged view of a portion of the inner sidewall of a middle annulus of a split floating ring embodiment of the present invention;
FIG. 5 is an enlarged view of a portion of the inner sidewall of a middle annulus in a split floating ring embodiment of the present invention;
FIG. 6 is a block diagram of a third ring of a split floating ring embodiment of the present invention;
FIG. 7 is an enlarged view of a portion of the inner sidewall of a middle annulus in a third embodiment of a split floating ring of the present invention;
FIG. 8 is a block diagram of a fourth ring of the split floating ring embodiment of the present invention.
The invention is further described below with reference to the drawings and examples.
Detailed Description
Split floating ring, rotary shaft sealing device, compressor and air conditioner embodiment one:
The air conditioner of this embodiment adopts the compressor of this embodiment, and the compressor of this embodiment adopts the pivot sealing device of this embodiment, and the pivot sealing device of this embodiment includes frame, pivot 200 and the split floating ring 100 of this embodiment, and split floating ring 100 installs in the frame, and split floating ring 100 overlaps on pivot 200, and the axial displacement of frame restriction split floating ring 100 along pivot 200, the rotation of frame restriction floating ring around pivot 200, of course also can overlap the split floating ring 100 of establishing different quantity according to different sealing demands on same pivot 200.
Referring to fig. 1 to 3, the split floating ring 100 of the present embodiment includes an elastic pull ring 102 and three ring segments 101 with equal radian, wherein the three ring segments 101 are a first ring segment 101a, a second ring segment 101b and a third ring segment 101c, and the three ring segments 101 are sequentially connected in series end to end in the circumferential direction to form a ring body.
Referring to fig. 3, the ring segment 101 has a first circumferential end surface 117 and a second circumferential end surface 118 along two circumferential ends of the ring body, wherein a male plug 114 protrudes from the first circumferential end surface 117 along the circumferential direction of the ring body, a female plug 115 protrudes from the second circumferential end surface 118 along the circumferential direction of the ring body, the female plug 115 includes an inner joint 1151 and an outer joint 1152 spaced apart along the radial direction of the ring body, and a plug groove 1153 is formed between the inner joint 1151 and the outer joint 1152; along the axial direction of the ring body, the inner joint 1151 is located at one end on the second circumferential end surface 118, the other end of the second circumferential end surface 118 is a notch 1154, and the male joint 114 protrudes inward of the ring by a protrusion 1141.
Referring to fig. 1 and 2, the male connector 114a of the first ring segment 101a is cooperatively connected with the female connector 115b of the second ring segment 101b, the male connector of the second ring segment 101b is cooperatively connected with the female connector of the third ring segment 101c, the male connector of the third ring segment 101c is cooperatively connected with the female connector of the first ring segment 101a, the second ring segment 101b and the third ring segment 101c are mutually connected in the same manner, and the connection manner between the ring segments 101 is described below by taking the connection of the first ring segment 101a and the second ring segment 101b as an example, the male connector 114a of the first ring segment 101a is inserted into the insertion groove of the second ring segment 101b, and the protrusion 1141a on the first ring segment 101a is inserted into the notch on the second ring segment 101 b; along the axial direction of the ring body, the protrusions 1141a of the first ring flap 101a are in contact with the inner joint 1151b of the second ring flap 101 b; in the radial direction of the ring body, the male plug 114a of the first ring segment 101a is in clearance fit with the inner joint 1151b of the second ring segment 101b, and the male plug 114a of the first ring segment 101a is in clearance fit with the outer joint 1152b of the second ring segment 101 b. The clearance fit mode of the male plug 114 and the female plug 115 enables the ring segments 101 to mutually stagger along the circumferential direction so as to meet the requirement that the spacing between the split floating ring 100 and the rotating shaft 200 in the radial direction can be changed.
Referring to fig. 1 and 2, in order to ensure that the first ring lobe 101a and the second ring lobe 101b can move relative to each other along the circumferential direction of the ring body, the male connector 114a and the protrusion 1141a each have a gap between the second circumferential end surface of the second ring lobe 101b along the circumferential direction of the ring body, the inner connector 1151b and the outer connector 1152b each have a gap between the first circumferential end surface of the first ring lobe 101a along the circumferential direction of the ring body, the protrusion 1141a covers the gap between the inner connector 1151b and the first circumferential end surface of the first ring lobe 101a, and the inner connector 1151b covers the gap between the protrusion 1141a and the second circumferential end surface of the second ring lobe 101b, so that leakage of fluid along the gap between the inner connector 1151b and the first circumferential end surface of the first ring lobe 101a is avoided. Preferably, the clearance between the first ring lobe 101a and the second ring lobe 101b in the circumferential direction is 0.1 to 1mm, i.e., the clearance between the male plug 114a and the second circumferential end face of the second ring lobe 101b is 0.1 to 1mm, the clearance between the boss 1141a and the second circumferential end face of the second ring lobe 101b is 0.1 to 1mm, the clearance between the inner joint 1151b and the first circumferential end face of the first ring lobe 101a is 0.1 to 1mm, and the clearance between the outer joint 1152b and the first circumferential end face of the first ring lobe 101a is 0.1 to 1 mm.
Referring to fig. 3, the inner side wall of the ring segment 101 is provided with a first circumferential dam 111, a second circumferential dam 112 and a circumferential groove 113, the first circumferential dam 111 and the second circumferential dam 112 are located at two ends of the inner side wall of the ring segment 101 along the axial direction of the ring body, the circumferential groove 113 is formed between the first circumferential dam 111 and the second circumferential dam 112, and a distance h1=0.3 mm is provided between the inner side wall surface of the first circumferential dam 111 and the bottom wall of the circumferential groove 113 along the radial direction of the ring body; the outer diameter of the ring flap 101 is 100 mm, the width of the first circumferential dam 111 is 5mm, the width of the circumferential groove 113 is 10mm, and the width of the second circumferential dam 112 is 5mm in the axial direction of the ring body.
Alternatively, the width of the first circumferential dam 111 ranges from 1 to 10 mm, and the width of the second circumferential dam 112 ranges from 1 to 10 mm.
Alternatively, the pitch h1 ranges from 0.1 to 1 millimeter.
Regarding each dimension parameter of the split floating ring 100, it is required to specifically set according to the sealing requirement, and the greater the widths of the first annular dam 111, the second annular dam 112 and the annular groove 113, the better the sealing effect of the split floating ring 100.
Referring to fig. 1, each first annular dam 111 encloses a first annular dam, each second annular dam 112 encloses a second annular dam, and each annular groove 113 encloses an annular groove.
Referring to fig. 3 and 4, a plurality of circular blind holes 1131 are formed in the bottom wall of the circumferential groove 113, the depth direction of the circular blind holes 1131 is along the radial direction of the ring body, the diameter of the circular blind holes 1131 is 0.8 mm, the depth of the circular blind holes 1131 is 0.8 mm, each circular blind hole 1131 is distributed on the bottom wall of the circumferential groove 113 in an array manner, and 8 rows of circular blind holes 1131 are arranged along the axial direction of the ring body.
Referring to fig. 3, the outer peripheral wall of the ring segments 101 is provided with mounting grooves 116 extending along the circumferential direction of the ring body, the elastic pull ring 102 is sleeved on the mounting grooves 116 of each ring segment 101, and each ring segment 101 abuts against the inner side of the elastic pull ring 102.
Referring to fig. 1 and2, along the axial direction of the ring body, one side of the split floating ring 100 is a high pressure side, and the other side of the split floating ring 100 is a low pressure side; when the rotating shaft 200 is static, each ring flap 101 is tightly held on the rotating shaft 200 under the extrusion of the elastic pull ring 102, each first annular dam 111 is in sealing and abutting joint with the peripheral wall of the rotating shaft 200, and each second annular dam 112 is in sealing and abutting joint with the peripheral wall of the rotating shaft 200; when the rotating shaft 200 starts to rotate, the rotating shaft 200 drives the fluid in each annular groove 113 to rotate along the circumferential direction of the ring body, and as the circular blind holes 1131 are arranged on the bottom wall of the annular groove 113, the fluid generates dynamic pressure effect when flowing through the circular blind holes 1131, the dynamic pressure effect causes the split floating ring 100 to be quickly separated from contact with the rotating shaft 200, so that the split floating ring 100 is prevented from being rubbed with the rotating shaft 200 for a long time, the abrasion of the split floating ring 100 is reduced, and the abrasion of the rotating shaft 200 is reduced; in addition, when the fluid flows through the circular blind holes 1131, a vortex phenomenon is generated in the circular blind holes 1131, so that kinetic energy of the fluid is converted into heat energy to be dissipated, the resistance of the fluid to flow is increased, a throttling effect is generated, and leakage of the fluid is reduced; in addition, the side wall of the annular groove 133 has an annular flow guiding function, and fluid in the annular groove 113 is guided by the annular groove 113 and driven by the rotating shaft 200 to deflect in the flow direction, so that part of fluid flows along the circumferential direction of the annular groove 113, the flow blocking effect of the split floating ring 100 on the split floating ring 100 is further enhanced, the sealing effect of the split floating ring 100 is improved, and the leakage of the fluid is reduced.
When the rotating shaft 200 starts to rotate, friction is generated between the rotating shaft 200 and the ring segments 101, under the friction action of the rotating shaft 200, the ring segments 101 overcome the tensile force of the elastic pull ring 102 to generate displacement fluctuation in the radial direction of the ring body, and part of the position of the split floating ring 100 is not in sealing contact with the rotating shaft 200, so that fluid at the high pressure side of the split floating ring 100 enters the annular groove 113, the high pressure fluid enters the annular groove 113 to be more beneficial to generating dynamic pressure effect, the split floating ring 100 is more beneficial to being separated from the rotating shaft 200, the abrasion of the split floating ring 100 is more beneficial to being reduced, and the abrasion of the rotating shaft 200 is also beneficial to being reduced; in addition, the high-pressure fluid generates a vortex phenomenon in the round blind hole 1131, which is more beneficial to increasing the resistance of the fluid flow, generating a throttling effect and reducing the leakage of the fluid.
In addition, after the split floating ring 100 is separated from the rotating shaft 200, due to the sealing effect of the annular groove 113 and the circular blind hole 1131 on the bottom wall thereof, the distance between the first annular dam and the rotating shaft 200 in the technical scheme can be set to be larger than the distance between the inner wall of the floating ring and the rotating shaft 200 in the prior art under the condition of requiring the same sealing performance, which is beneficial to reducing the abrasion of the split floating ring 100 in the running state and reducing the abrasion of the rotating shaft 200.
Alternatively, the number of ring segments 101 need not be three, but may be two, four, etc.
Alternatively, the circular blind holes 1131 may be replaced by triangular holes, diamond holes, square holes, rectangular holes, etc., which can also achieve the purpose of the invention.
Split floating ring, rotary shaft sealing device, compressor and air conditioner embodiment II:
Referring to fig. 5, in the first embodiment, the circular blind holes 1131 are omitted, and the bottom wall of the circumferential groove 113 is provided with the elliptical blind holes 1132, and the arrangement of the elliptical blind holes 1132 on the bottom wall of the circumferential groove 113 can refer to the arrangement of the circular blind holes 1131 in the first embodiment.
Referring to fig. 5, the rotating shaft 200 rotates around a direction a, a direction b is an axial direction of the rotating shaft 200, a positive side of the ring segment 101 along the direction b is a high pressure side, and a negative side of the ring segment 101 along the direction b is a low pressure side.
The major axis direction of the oval blind holes 1132 is the direction of spiral around the ring body, and the spiral direction of the major axis of each oval blind hole 1132 is the same. The major axis of the elliptical blind hole 1132 forms an acute angle with the rotation direction a of the shaft 200 from the low pressure side to the high pressure side. Thus, when the shaft 200 rotates, the elliptical blind holes 1132 guide the fluid to the high pressure side along the long axis direction (as indicated by arrow c1 in fig. 5), further reducing the leakage of the fluid and improving the sealing performance of the split floating ring 100.
The split floating ring, the rotating shaft sealing device, the compressor and the rest of the air conditioner in the second embodiment are the same as those in the first embodiment.
Split floating ring, rotary shaft sealing device, compressor and air conditioner embodiment III:
referring to fig. 6, in the first embodiment, the circular blind hole 1131 is omitted, and the bottom wall of the circumferential groove 113 is provided with the strip grooves 1133, the length direction of the strip grooves 1133 is the direction of winding the ring body, the spiral direction of each strip groove 1133 is the same, and each strip groove 1133 is distributed along the circumferential direction of the ring body.
Referring to fig. 7, the rotating shaft 200 rotates around a direction a, a direction b is an axial direction of the rotating shaft 200, a positive side of the ring segment 101 along the direction b is a high pressure side, and a negative side of the ring segment 101 along the direction b is a low pressure side.
The direction in which the bar-shaped groove 1133 spirals from the low pressure side to the high pressure side makes an acute angle with the rotation direction a of the rotation shaft 200. Thus, when the rotation shaft 200 rotates, the strip grooves 1133 guide the fluid to the high pressure side in the longitudinal direction (as indicated by arrow c2 in fig. 7), further reducing the leakage of the fluid, and improving the sealing performance of the split floating ring 100.
The split floating ring, the rotating shaft sealing device, the compressor and the rest of the air conditioner in the third embodiment are the same as those in the first embodiment.
Split floating ring, rotary shaft sealing device, compressor and air conditioner embodiment IV:
Referring to fig. 8, in the first embodiment, the circular blind hole 1131 is omitted, and the annular throttling grooves 1134 are disposed on the bottom wall of the annular groove 113, and each annular throttling groove 1134 is axially distributed along the ring body. The annular throttling groove 1134 can improve dynamic pressure opening performance of the split floating ring, and the annular throttling groove 1134 is convenient to process.
Specifically, the groove wall thickness between each annular throttle groove 1134 is 0.1 to 0.7 mm in the axial direction of the ring body.
The split floating ring, the rotary shaft sealing device, the compressor and the rest of the air conditioner in the fourth embodiment are the same as those in the first embodiment.
Finally, it should be emphasized that the foregoing description is merely illustrative of the preferred embodiments of the invention, and that various changes and modifications can be made by those skilled in the art without departing from the spirit and principles of the invention, and any such modifications, equivalents, improvements, etc. are intended to be included within the scope of the invention.
Claims (17)
1. The split floating ring is used for being sleeved on the rotating shaft and comprises at least two ring petals, the ring petals are connected in series to form a ring body, and two adjacent ring petals are movably connected;
The method is characterized in that:
The annular ring comprises a ring body and is characterized in that a first annular dam, a second annular dam and an annular groove are formed in the inner side wall of the ring body, a concave area is formed in the bottom wall of the annular groove, and the annular groove is formed between the first annular dam and the second annular dam along the axial direction of the ring body;
each first annular dam forms a first annular dam, each second annular dam forms a second annular dam, and each annular groove forms an annular groove;
The concave region extends around the spiral direction of the ring body, two axial sides of the ring body are respectively a high-pressure side and a low-pressure side, and the concave region clamps an acute angle between the spiral direction of the low-pressure side and the high-pressure side and the rotating direction of the rotating shaft.
2. The split floating ring of claim 1, wherein:
Elastic pull rings are sleeved on the ring body along the circumferential direction, and each ring flap is extruded on the inner side of each elastic pull ring.
3. The split floating ring of claim 2, wherein:
the outer peripheral wall of the ring body is provided with a mounting groove which surrounds the ring body in a circle, and the elastic pull ring is sleeved in the mounting groove.
4. The split floating ring of claim 1, wherein:
The distance between the bottom wall of the annular groove and the inner wall of the first annular dam is 0.1 to 1 mm, and/or the distance between the bottom wall of the annular groove and the inner wall of the second annular dam is 0.1 to 1 mm, in the radial direction of the ring body.
5. The split floating ring of claim 1, wherein:
Along the circumferential direction of the ring body, one end of the ring valve is provided with an inserting joint, and the other end of the ring valve is provided with an inserting groove;
In the two adjacent ring petals, the plug connector of one ring petal is inserted into the plug groove of the other ring petal, and the plug connector and the groove wall of the plug groove are in clearance fit in the radial direction of the ring body.
6. The split floating ring as claimed in claim 5, wherein:
Along the radial direction of the ring body, the inner side of the plug-in groove is provided with an inner side joint, the outer side of the plug-in groove is provided with an outer side joint, the inner side joint is provided with a notch which penetrates through the inner side wall of the ring body, and the plug-in joint is provided with a bulge protruding inwards;
In two adjacent ring petals, the bulge of one ring petal is inserted into the notch on the inner side joint of the other ring petal, and the bulge covers the circumferential gap of the inner side joint of the two ring petals along the axial direction of the ring body.
7. The split floating ring of claim 1, wherein:
The number of ring petals is 3 to 5.
8. The split floating ring of claim 1, wherein:
The concave area occupies 0.05 to 0.5 of the total area of the bottom wall of the annular groove.
9. The split floating ring of claim 1, wherein:
the depth of the recessed area is 0.1 to 1 mm.
10. Split floating ring according to any one of claims 1 to 9, characterized in that:
The concave area is a strip-shaped groove, and the length direction of the strip-shaped groove is the direction around the ring body spiral.
11. Split floating ring according to any one of claims 1 to 9, characterized in that:
The concave area is the blind hole, the blind hole is equipped with the multirow, and each row the interval direction of blind hole is followed the axial of ring body, each blind hole of same row is followed the circumference distribution of ring body.
12. The split floating ring as claimed in claim 11, wherein:
the blind holes are elliptical holes, and the long axis direction of the elliptical holes is the direction around the ring body in a spiral mode.
13. The split floating ring as claimed in claim 11, wherein:
the blind holes are round holes, and the ratio of the depth of each round hole to the aperture of each round hole is 0.1-5.
14. Split floating ring according to any one of claims 1 to 9, characterized in that:
the concave area is an annular throttling groove extending along the circumferential direction of the ring body, and the annular throttling grooves are distributed along the axial direction of the ring body.
15. Rotating shaft sealing device, including the pivot, its characterized in that:
Further comprising a split floating ring as claimed in any one of claims 1 to 14, said split floating ring being sleeved on said shaft.
16. The compressor is characterized in that:
A spindle seal comprising the apparatus of claim 15.
17. An air conditioner, characterized in that:
Comprising a compressor according to claim 16.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910355003.XA CN110056531B (en) | 2019-04-29 | 2019-04-29 | Split floating ring, rotating shaft sealing device, compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910355003.XA CN110056531B (en) | 2019-04-29 | 2019-04-29 | Split floating ring, rotating shaft sealing device, compressor and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110056531A CN110056531A (en) | 2019-07-26 |
| CN110056531B true CN110056531B (en) | 2024-05-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910355003.XA Active CN110056531B (en) | 2019-04-29 | 2019-04-29 | Split floating ring, rotating shaft sealing device, compressor and air conditioner |
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| Country | Link |
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| CN (1) | CN110056531B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110578558B (en) * | 2019-10-22 | 2024-07-19 | 浙江工业大学 | Container type hole type damping seal with flange damping holes and suitable for bidirectional rotation |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19506683A1 (en) * | 1995-02-25 | 1996-09-05 | Neuman & Esser | Piston rod seal for reciprocating piston machines |
| JPH11280910A (en) * | 1998-03-30 | 1999-10-15 | Senshin Zairyo Riyo Gas Generator Kenkyusho:Kk | Cylindrical surface seal device |
| WO2017146136A1 (en) * | 2016-02-23 | 2017-08-31 | 三菱重工コンプレッサ株式会社 | Sealing device and rotating machine |
| CN209724767U (en) * | 2019-04-29 | 2019-12-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Divide valve floating ring, shaft sealing device, compressor and air conditioner |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9638326B2 (en) * | 2014-12-15 | 2017-05-02 | Kaydon Ring & Seal, Inc. | Arch-bound ring seal and ring seal system including an arch-bound ring seal |
-
2019
- 2019-04-29 CN CN201910355003.XA patent/CN110056531B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19506683A1 (en) * | 1995-02-25 | 1996-09-05 | Neuman & Esser | Piston rod seal for reciprocating piston machines |
| JPH11280910A (en) * | 1998-03-30 | 1999-10-15 | Senshin Zairyo Riyo Gas Generator Kenkyusho:Kk | Cylindrical surface seal device |
| WO2017146136A1 (en) * | 2016-02-23 | 2017-08-31 | 三菱重工コンプレッサ株式会社 | Sealing device and rotating machine |
| CN209724767U (en) * | 2019-04-29 | 2019-12-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Divide valve floating ring, shaft sealing device, compressor and air conditioner |
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| Publication number | Publication date |
|---|---|
| CN110056531A (en) | 2019-07-26 |
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