EP0704624B1 - Turbo-compresseur - Google Patents

Turbo-compresseur Download PDF

Info

Publication number
EP0704624B1
EP0704624B1 EP95115153A EP95115153A EP0704624B1 EP 0704624 B1 EP0704624 B1 EP 0704624B1 EP 95115153 A EP95115153 A EP 95115153A EP 95115153 A EP95115153 A EP 95115153A EP 0704624 B1 EP0704624 B1 EP 0704624B1
Authority
EP
European Patent Office
Prior art keywords
drive motor
stage compressor
chamber
compressor
gear unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95115153A
Other languages
German (de)
English (en)
Other versions
EP0704624A1 (fr
Inventor
Kazumitsu Hasegawa
Yujiroh Matsubayashi
Kazuo Ashizawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHI Corp
Original Assignee
IHI Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP23388294A external-priority patent/JP3470410B2/ja
Priority claimed from JP23546294A external-priority patent/JP3385745B2/ja
Application filed by IHI Corp filed Critical IHI Corp
Publication of EP0704624A1 publication Critical patent/EP0704624A1/fr
Application granted granted Critical
Publication of EP0704624B1 publication Critical patent/EP0704624B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger

Definitions

  • the present invention relates to a turbo compressor used in a factory for power source and processing, and more particularly to a turbo compressor which has a reduced size and is easier for maintenance.
  • the two-step type turbo compressor is known wherein fluid is compressed by its first stage compressor at the first step and further compressed by its second stage compressor at the second step, then eventually discarded.
  • the impellers of the first and second stage compressors are linked with a rotary shaft which is rotated by a drive motor by way of a gear unit.
  • the rotary shaft is arranged in parallel with the output shaft of the drive motor, wherein a gear of the gear unit is engaged with a gear in the middle of the rotary shaft, and an impeller of the second stage compressor is mounted at one end of the rotational shaft on the drive motor's side, while an impeller of first stage compressor is mounted at the other end of the shaft.
  • a turbo compressor according to the preamble of claim 1 is known from US 3 476 485.
  • the first object of the present invention proposed in consideration with the problems above is to provide a turbo compressor which allows size-reduction by introducing new arrangement of components.
  • the second object of the present invention is to provide a turbo compressor which allows compressors and a gear unit to be replaced with new ones without demanding the removal of a drive motor.
  • the turbo compressor has an arrangement in which a rotational shaft with a first stage compressor connected at one end and a second stage compressor connected at the other end is located in parallel with an output shaft of a drive motor by way of a gear unit, wherein the first stage compressor is located at the end of the rotational shaft which is on the drive motor's side while the second stage compressor is located at the other end of the rotational shaft, and an air inlet tube and an air inlet filter of the first stage compressor are located proximate to and in parallel with a side of the drive motor parallel to the output shaft of the drive motor.
  • a substantially rectangular-parallelepiped box of which inside is divided into two cooling chambers is provided underneath the first stage compressor, the second stage compressor and the gear unit, wherein one of the cooling chambers may be provided with a heat exchanger for an intercooler which cools a fluid emitted from the first stage compressor down then introduces the fluid into the second stage compressor, while the other cooling chamber may be provided with a heat exchanger for aftercooler which cools the fluid emitted from the second stage compressor down and then emits it out.
  • Each ofthe heat exchangers is elongated in the longitudinal direction along the associated cooling chamber, wherein each heat exchanger is located in the middle of the associated cooling chamber defining an entrance chamber and an exit chamber according to the flow direction.
  • An air inlet with an elongated shape may be formed along each heat exchanger on one longitudinal end of the entrance chamber while an air outlet may be formed on the longitudinally opposite end ofthe exit chamber.
  • the turbo compressor has an arrangement in which a rotary shaft is located in parallel with a output shaft ofthe drive motor by way of a gear unit, wherein the first stage compressor is located at one end of the rotational shaft which end is on the drive motor's side while the second stage compressor is located at the other end of the rotational shaft, a distance between the output shaft and the rotational shaft is shortened so that the periphery of the drive motor and that of the first stage compressor partially overlap each other, the gear unit is integrally formed with the casing ofthe first stage compressor, and recesses are formed in the drive motor itselfas well as in the drive motor mounting flange of the casing for the convenience in axially removing the inlet block ofthe first stage compressor.
  • a window portion may be provided for exposing a shaft coupling which connects the output shaft of the drive motor and the input shaft of the gear unit.
  • the structure according to the first aspect allows an arrangement in which the first stage compressor is located on the drive motor's side while the second stage compressor is located on the opposite side, and the air inlet tube and the air inlet filter of the first stage compressor are located proximate to and in parallel with a side of the drive motor.
  • This arrangement prevents the air inlet tube and the air inlet filter from projecting outwardly, enabling a substantially rectangular installation area ofthe turbo compressor as a whole, which results in size-reduction. That is, the arrangement in which the first and second stage compressors, the gear unit, the drive motor, the air inlet tube and the air inlet filter ofthe first stage compressor form a substantially rectangular installation area as viewed from the top reduces the installation area ofthe whole apparatus.
  • the structure according to the second aspect allows an arrangement in which the heat exchanger for the intercooler and the heat exchanger for the aftercooler are accommodated in a substantially rectangular-parallelepiped box provided underneath the first and the second stage compressors and the gear unit.
  • This arrangement reduces the size of the whole structure of the turbo compressor including the cooling mechanism. That is, the two story structure wherein the cooling mechanism is provided in the first story section ofthe box while the compression mechanism as well as the drive mechanism that drives the compression mechanism are located in the second story section, reduces the size ofthe whole structure ofthe apparatus (a turbo compressor).
  • the structure according to the third aspect allows an arrangement in which the air entrance with an elongated shape is formed on one longitudinal end of the associated entrance chamber along each heat exchange, while the air exit is formed on the longitudinally opposite end of the associated exit chamber.
  • This arrangement achieves a substantially even flow of the fluid through the heat exchanger as the fluid introduced into the entrance chamber from the air entrance flows to the exit chamber to be eventually emitted out ofthe emission vent, and the even flow of the fluid improves the heat exchange rate. That is, the arrangement wherein the elongated-shaped air entrance is formed at one longitudinal end of the associated entrance chamber along each heat exchange while the air exit is formed at the longitudinally opposite end ofthe associated exit chamber achieves a substantially even flow ofthe fluid through the heat exchanger, thus improving the heat exchange.
  • the structure according to the fourth aspect provides the recesses with the casing and the drive motor respectively, and each recess prevents the inlet block and the motor to interfere with each other when the inlet block of the first stage compressor is axially displaced for removal.
  • the inlet block ofthe first stage compressor can be removed without removing the drive motor from the drive motor mounting flange of the casing, which considerably facilitates the maintenance of the gear unit and the like.
  • the structure according to the fifth aspect allows the shaft coupling that connects the output shaft of the drive motor with the input shaft of the gear unit to be exposed through the window portion provided in the gear casing.
  • the window portion allows the shaft coupling to be disconnected through the window portion and thus the gear unit to be removed without dismounting the drive motor, which considerably facilitates the maintenance of the gear unit and the like.
  • Fig. 1 is a plan view of a turbo compressor in accordance with the first aspect of the present invention.
  • Fig. 2 is its side view and Fig. 3 is its front view.
  • a rotary shaft 4 is arranged in parallel with a output shaft 2 of a drive motor 1 by way of a gear unit 3 between the two shafts.
  • a first stage compressor 5 is provided at one end of the rotary shaft 4 which is on the drive motor's 1 side, while a second stage compressor 6 is provided at the other end ofthe rotary shaft 4.
  • An air inlet tube 7 and an air inlet filter 8 ofthe first stage compressor 5 is located in parallel with a side of the drive motor 1 parallel to the output shaft of the drive motor.
  • the drive motor 1 is so-called a flange motor mounted to a gear case 9 of the gear unit 3 by way of flange 10 and its output shaft 2 is connected to a gear shaft 11 of the gear unit 3 (shown in Fig. 4) with bolt and nut through a shaft coupling 12.
  • the gear shaft 11 is rotatably supported in the gear case 9 through bearings 13 with a larger gear 14 mounted in the middle of the gear shaft 11.
  • the larger gear 14 is engaged with a smaller gear 15 mounted on the rotary shaft 4.
  • the rotation velocity of the output shaft 2 ofthe drive motor 1 is increased and transmitted to the rotary shaft 4 by the gear unit 3.
  • the rotary shaft 4 has the smaller gear 15 mounted in the middle, an impeller 16 of the first stage compressor 5 at one end which is on the drive motor's 1 side, and an impeller 17 of the second stage compressor 6 at the other end.
  • the portion between the smaller gear 14 and the impeller 16, as well as the portion between the smaller gear 14 and the impeller 17 are supported in the gear case 9 through bearings 18.
  • the impeller 16 ofthe first stage compressor 5 is accommodated in a cylindrical recess 19 formed in a side of the gear case 9, while the impeller 17 of the second stage compressor 6 is accommodated in a cylindrical recess 20 formed in the opposite side ofthe gear case 9.
  • Blocks 25, 26 having scroll chambers 21,22 and air inlet passages 23, 24 are inserted in these recesses 19, 20, respectively.
  • Diffusers 27, 28 are formed between the block 25 and the recess 19 as well as between the block 26 and the recess 20, respectively.
  • the impeller 16 of the first stage compressor 5 draws in air from the air inlet passage 23 and radially and outwardly increases the flow velocity of the air.
  • the air which is cooled down in the intercooler 29 is led to a link passage 30 to the second stage compressor 6.
  • the link passage 30 is spirally formed outside the scroll chamber 22 of the second stage compressor 6, and defined when a cover 31 covers the recess 20.
  • the gear case 9 is separable into the upper part (the cover, not shown) and the lower part (the case body) by a horizontal sectional plane shown in Fig. 4.
  • the cover can be mounted to the case body with bolts by screwing the bolts into apertures 34.
  • the cover 31 and the block 26 of the second stage compressor 6 as well as the block 25 of the first stage compressor 5 can be removed by unscrewing bolts 35.
  • a crescent-shaped portion is cut off from the motor mounting flange 36 in the gear case 9, thus defining a recess 37 so that the block 25 of the first stage compressor 5 can be pulled out without removing the drive motor 1.
  • another recess 38 of minimum length required for pulling the block 25 out is formed in the drive motor 1 itself.
  • the air inlet tube 7 and the air inlet filter 8 are connected with the inlet passage 23 of the first stage compressor 5.
  • the inlet tube 7 and the inlet filter 8 are located in parallel with the side of the drive motor 1.
  • the inlet tube 7 is S-curved in the plan view and connected with the air inlet filter 8 by way of an inlet control valve 39.
  • the inlet filter 8 includes a casing 40 which has a reversed L-shape in the side view as shown in Fig. 2, and functions for removing dusts from the sucked air as well as for muting the noise during suction.
  • An air inlet 41 ofthe drive motor 1 and an air outlet 42 ofthe drive motor 1 are also shown in Fig. 1.
  • a substantially rectangular-parallelepiped box 46 which is located underneath the first stage compressor 5, the second stage compressor 6 and the gear unit 3 is integrally molded with the gear case 9.
  • the box is separated into a cooling chamber 44 containing the intercooler 29 and a cooling chamber 45 containing the aftercooler 33 by a partition wall 43.
  • a heat exchanger 47 for the intercooler 29 is provided so that the air from the first stage compressor 5 can be cooled by the intercooler 29 prior to its being led to the second stage compressor 6.
  • a heat exchanger 48 for the aftercooler 33 is provided so that the air from the second stage compressor 6 can be cooled and then emitted out.
  • the substantially rectangular-parallelepiped box 46 having two cooling chambers 44, 45 is integrally molded with the gear case 9, and functions as a base which supports the first stage compressor 5, the second stage compressor 6, the gear unit 3, the drive motor 1 and the inlet filter 8.
  • the box is so formed as to have an installation area (an installation area viewed from the top) which corresponds to the substantially rectangular installation area of the compressor 5 and other parts.
  • each of the heat exchangers 47, 48 is formed with a longitudinally elongated shape along the associated cooling chamber 44, 45, and is located in the middle of the associated chamber 44, 45 dividing the chamber into an entrance chamber 49 and an exit chamber 50, respectively.
  • a gap exists between the top/bottom of each heat exchanger 47, 48 (seal baffles 58) and the inner surface of the associated cooling chamber 44, 45.
  • An air entrance 51 having an longitudinally elongated rectangular shape is provided, at one longitudinal end of the associated entrance chamber 49 along each heat exchanger 47, 48 respectively, while an exit 52 is provided on the longitudinally opposite end of the associated exit chamber 50 along each heat exchanger 47,48 respectively.
  • the air entrance 51 of the cooling chamber 44 containing the intercooler 29 is connected to the scroll chamber 21 of the first stage compressor 5, while the exit 52 of the cooling chamber 44 is connected to the link passage 30 of the second stage compressor 6.
  • the air entrance 51 of the cooling chamber 45 containing the aftercooler 33 is connected to the scroll chamber 22 ofthe second stage compressor 6 while the exit 52 ofthe cooling chamber 45 is connected to an emission tube 53.
  • Fig. 6 shows a plan view of the cooling chamber 45 containing the aftercooler 33.
  • the cooling chamber 45 of which installation area is rectangular in the plan view is divided into the entrance chamber 49 and the exit chamber 50 by the heat exchanger 48 for the aftercooler 33 which has an elongated shape.
  • An air entrance 51 with an elongated rectangular shape is provided at one longitudinal end of the associated entrance chamber 49 along the heat exchanger 48.
  • the air entrance 51 is connected to the scroll chamber 22 of the second stage compressor 6 by way of a link passage 55 of which cross section becomes larger as it approaches the air entrance as shown in Fig. 5.
  • an exit 52 is provided at the longitudinally opposite end of the associated entrance chamber 50.
  • the exit 52 is connected to an emission tube 53 which is integrally molded with a side of the box 46.
  • An emission vent 56 is formed at the fee end ofthe emission tube 53.
  • the heat exchangers 47, 48 are provided with: a plurality of fin plates 57 oriented so that they vertically intersect the longitudinal axis of the exchangers; a plurality of water pipes which penetrate and extend through the fin plates 57 (not shown); seal baffles 58 extending both upon and beneath the fin plates 57; and seal members 59 mounted to the seal baffles 58.
  • the seal baffle 58 guides the introduced air from one side to the other of the heat exchangers 47,48, and the seal members 59 seal the gaps between the seal baffles 58 and the inner surface of the cooling chambers 44, 45, preventing the air from leaking through the gaps.
  • the seal members now clearly divides each cooling chamber 44, 45 into the entrance chamber 49 and the exit chamber 50.
  • an oil chamber 60 is integrally molded with the box 46.
  • the oil chamber 60 reserves oil for lubricating the components in the gear unit 3 such as the larger and the smaller gears 14, 15, the rotary shaft 4 on which the impellers 16, 17 are mounted, and the like.
  • the level of oil surface inside the oil chamber 60 is indicated by an oil level gauge 6, while the oil pressure is indicated by a manometer 62 as shown in Fig. 2.
  • the oil in the oil chamber 60 is pumped up through an oil tube 63 by a main oil pump 64 that is directly coupled with the gear shaft 11, and reaches the oil cooler 66 through an oil tube 65. After cooled, the oil is supplied to the bearings 18 of the rotary shaft 4 and the like through the oil tube 67. The supplied oil is eventually retrieved into the oil chamber 60.
  • a sub oil pump 68 is also illustrated in Fig. 1-Fig. 3. The sub oil pump 68 is driven by its own motor 69 prior to the starting ofthe drive motor 1 which drives the main oil pump 64, in order to send a preliminary supply of oil to the bearings 18 of the rotary shaft 4 and the like.
  • the first stage compressor 5 is located on the drive motor's side while the second stage compressor 6 is located on the opposite side, and the air inlet tube 7 and the air inlet filter 8 ofthe first stage compressor 5 are located in parallel with the side ofthe drive motor 1.
  • This arrangement in contrast with that of the prior art, prevents the air inlet tube 7 and the air inlet filter 8 from projecting out of the frame of the casing, achieving a substantially rectangular installment area which is 25% smaller than the previously required, thus reducing the whole size ofthe turbo compressor.
  • the box 46 functions not only as an accommodating box of the cooling mechanism such as the intercooler 29, but also as a support base of the compressor 5 and the like.
  • the turbo compressor of the present invention has a two-story structure in which the heat exchangers 47, 48 as the cooling mechanism are provided in the first story (more precisely in the box 46), while the compressors 5, 6 as the compression mechanism and the drive motor 1 as the drive mechanism which drives the compressors are provided in the second story.
  • This two-story structure allows the size-reduction of the turbo compressor as a whole.
  • the box 46 can accommodate the oil storing chamber 60 in it, which also contributes to the size-reduction of the whole structure.
  • the arrangement in which the elongated rectangle-shaped air entrance 51 is formed at one longitudinal end of the associated entrance chamber 49 of each cooling chamber 44, 45 along each heat exchange 47, 48, and the further arrangement in which the air exit 52 is formed at the longitudinally opposite end of the exit chamber 50 are provided. These arrangements allow substantially even air flow through the heat exchangers 47, 48 when the air introduced from the air entrance 51 into the entrance chamber 49 flow to the exit chamber 50 and is eventually emitted out of the exit 52. The substantially even air flow through the heat exchangers 47, 48 improves the heat exchanger rate.
  • a rotary shaft 104 is arranged in parallel with a output shaft 102 of a drive motor 100 by way of gear unit 103 between the two shafts.
  • a first stage compressor 105 is provided at the end of the rotary shaft 104 which end is on the drive motor's 100 side, while a second stage compressor 106 is provided at the other end of the rotary shaft 104.
  • An inlet tube 107 and an inlet filter 108 of the first stage compressor 105 are located in parallel with a side of the drive motor 100.
  • a drive motor 100 has at one edge a motor-side flange 109 (which corresponds to the drive motor mounting flange of claim 2).
  • the motor-side flange 109 is mounted to a casing -side flange 111 with bolt and nut, wherein the casing-side flange 111 is formed in a casing 110 which accommodates the gear unit 103 as shown in Fig. 8 and Fig. 9.
  • Bolt bores 112 are also shown in the drawings.
  • a output shaft 102 of the drive motor 100 is connected to an input shaft 114 of the gear unit 103 through a shaft coupling 115 with bolt and nut.
  • the input shaft 114 is rotatably supported in the casing 110 through bearings 116, with a larger gear 117 mounted in the middle of the input shaft 114.
  • the larger gear 117 is engaged with the smaller gear 118 which is provided on the rotary shaft 104.
  • the rotational velocity of the output shaft 102 of the drive motor 100 is increased and transmitted to the rotary shaft 104 by the gear unit 103.
  • the diameter of the smaller gear 118 has been reduced to the ultimately minimized size which is substantially the same as the shaft diameter of the rotary shaft 104, in order to achieve size-reduction by ultimately minimizing the distance between the gear shaft 114 and the rotary shaft 104.
  • the periphery of the drive motor 100 and that of the first stage compressor 105 overlap each other due to the ultimately shortened distance between the two shafts.
  • the rotary shaft 104 has the smaller gear 118 mounted in the middle, an impeller 119 of the first stage compressor 105 at one end which is on the drive motor's 100 side, and an impeller 120 of the second stage compressor 106 at the other end.
  • the portion between the smaller gear 118 and the impeller 119, as well as the portion between the smaller gear 118 and the impeller 120 are supported in the casing 110 through bearings 121.
  • the impeller 119 of the first stage compressor 105 is accommodated in a cylindrical recess 122 formed on a side of the casing 110, while the impeller 120 of the second stage compressor 106 is accommodated in a cylindrical recess 123 formed on the opposite side of the casing 110.
  • the casing 110 functions as a casing not only for the gear unit 103 but also for the compressors 105, 106.
  • Inlet blocks 128, 129 having scroll chambers 124, 125 and air inlet passages 126, 127 are inserted in the recesses 122, 123, respectively.
  • Diffusers 130, 131 are formed between the top of the block 25 and the base of the recess 122, as well as between the top of the inlet block 129 and the base ofthe recess 123, respectively.
  • the impeller 119 of the first stage compressor 105 draws in air from the air inlet passage 126 and radially and outwardly increases the flow velocity of the air.
  • the air with increased velocity passes through the diffuser 130 and the scroll chamber 124, its velocity is decreased and converted into pressure, then the air reaches an intercooler located in a box 132 shown in Fig. 7.
  • the box is integrally molded with the casing 110.
  • the air which is cooled down in the intercooler in the box 132 is lead to the link passage 133 of the second stage compressor 106.
  • the link passage 133 is spirally formed outside the scroll chamber 125 of the second stage compressor 106, and defined when a cover 134 covers the recess 123.
  • a disk-shaped passage 135 is formed between the cover 134 and the block 129.
  • the air inside the link passage 133 passes through the disk-shaped passage 135 and the inlet passage 127, then the impeller 120 of the second stage compressor 106 radially and outwardly increases the flow velocity of the air.
  • the air with increased velocity passes through the diffuser 131 and the scroll chamber 125, its velocity is converted into pressure then the air reaches an aftercooler accommodated in the box 132. The air is cooled down in the aftercooler and eventually emitted out.
  • the casing 110 is separable into the upper part (a cover, not show) and the lower part (the case body) by a horizontal sectional plane shown in Fig. 9.
  • the cover can be mounted to the case body with bolts by screwing the bolts into apertures 136.
  • maintenance of the input shaft 114, the larger gear 117, the smaller gear 118, the rotary shaft 104 and the impellers 119, 120 can be easily performed by removing the cover.
  • the cover 134 and the inlet block 129 of the second stage compressor 106 as well as the inlet block 128 of the first stage compressor 105 can be removed by unscrewing bolts 137.
  • a crescent-shaped portion is cut off from the case-side flange 111 on the casing 110 and from the motor-side flange 109 on the drive motor 100, defining recesses 138, 139 respectively, so that the inlet block 128 of the first stage compressor 105 can be pulled out without removing the drive motor 100.
  • another crescent-shaped recess 140 of minimum length required for pulling the inlet block 128 out is formed in the drive motor 100 itself.
  • a crescent-shaped cylindrical cover 141 is attached to the recess 140.
  • the cover 141 guides the inlet block 128 when the block is pulled out.
  • the front body 100a of the drive motor 100 which is provided with the recess 140 includes a motor emission vent 142 but does not accommodate any substantial rotary drive mechanism such as coils and electro-magnetics.
  • the substantial rotary drive mechanism is accommodated in the rear body 100b which is defined behind the flange 143 wherein the flange is located in the middle of the drive motor 100.
  • the motor emission vent 142 emits the cooled air which is drawn in from the motor air inlet 144 located in the rear body 100b of the drive motor 100.
  • a arc-shaped reinforcement rib 145 is formed along the recess 138 defined in the case-side flange 111 wherein the case-side flange 111 is provided in the casing 110.
  • the reinforcement rib 145 functions for compensating the loss of binding rigidity which results from the formation of the recess 138.
  • a grease injection tube 146 through which grease is injected into the bearings of the output shaft 102 of the drive motor 100 is shown in Fig. 11 along with a grease discard tube 147 which discards grease when a handle 148 is pulled to the left-hand side.
  • a window 149 is provided in the gear casing 110a which accommodates the gear unit 103 of the casing 110, wherein the window exposes the shaft coupling 115 which connects the output shaft 102 ofthe drive motor 100 and the input shaft 114 of the gear unit 103.
  • the window 149 is a rectangular-shaped opening on the upper surface of the case-side flange 111 of the gear casing 110a, and as shown in Fig. 7, upwardly exposes the shaft coupling 115 which connects the input shaft 114 of the gear unit 103 and the output shaft 102 of the drive motor 100.
  • a net member 150 for protection is releasably attached to the window 149.
  • the shaft coupling 115 which connects the output shaft 102 of the drive motor 100 and the input shaft 114 of the gear unit 103 is exposed in the window 149 provided in the casing 110a.
  • maintenance of each of the components constituting the gear unit 103 (such as the larger gear 117, the input shaft 114 and the like) will be easily performed because the gear unit including the shaft coupling 115 can solely be removed without moving the drive motor 100 on the case-side flange 111 of the casing 110.
  • the removal of the gear unit is, of course, preceded by removal of the net material 150 attached to the window 149, disconnection of the shaft coupling 115 through the window 149, and removal of the cover attached to the upper side of the body of which sectional view is horizontally taken and shown in Fig. 9. That is, the drive motor 100 which is heavy (weighs about 850 kg) and difficult to remove may remain attached to the casing 110, with its motor-side flange 109 connected to the case-side flange 111.
  • the inlet block 128 of the first stage compressor 105 when the inlet block 128 of the first stage compressor 105 is axially displaced for removal, the interference between the inlet block 128 and the drive motor 100 can be avoided owing to the three recesses wherein the three recesses are the recess 138 provided in the case-side flange 111, the recess 139 provided in the motor-side flange and the recess 140 provided on a side of the drive motor 140.
  • the inlet block 128 of the first stage compressor 105 can be removed without removing the drive motor 100 from the casing 110.
  • the maintenance of each component of the first and the second stage compressors 105, 106 may be performed without removing the drive motor 100 from the casing 110.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (5)

  1. Turbocompresseur dans lequel un arbre rotatif (4, 104), avec un compresseur de premier étage (5, 105) relié à une extrémité et un compresseur de deuxième étage (6, 106) relié à l'autre extrémité, est disposé parallèlement à un arbre de sortie (2, 102) d'un moteur d'entraínement (1, 100) au moyen d'une boíte à engrenages (3, 103), le compresseur de premier étage (5, 105) étant situé à une extrémité de l'arbre rotatif (4, 104), cette extrémité étant du côté du moteur d'entraínement, alors que le compresseur de deuxième étage (6, 106) est situé à l'autre extrémité de l'arbre rotatif (4, 104), caractérisé en ce qu'un tube d'admission d'air (7, 107) et un filtre d'admission d'air (8, 108) du compresseur de premier étage (5, 105) sont disposés proches de et parallèles à un côté du moteur d'entraínement (1, 100), parallèlement à l'arbre de sortie (2, 102) du moteur d'entraínement (1, 100).
  2. Turbocompresseur selon la revendication 1, caractérisé en ce que
       la distance entre l'arbre de sortie (102) et l'arbre rotatif (104) est raccourcie d'une manière telle que la périphérie du moteur d'entraínement (100) et la périphérie du compresseur de premier étage (105) se chevauchent partiellement l'une l'autre ;
       la boíte à engrenages (103) est formée d'une seule pièce avec un carter (110) du compresseur de premier étage (105) ; et
       des évidements (138, 139, 140) sont formés sur le moteur d'entraínement (100) lui-même ainsi que dans une bride de montage (111) du moteur d'entraínement du carter (110), à des fins de commodité du démontage axial d'un bloc d'admission (128) du compresseur de premier étage (105).
  3. Turbocompresseur selon la revendication 1, caractérisé en ce qu'une boíte (46) sensiblement en forme de parallélépipède rectangle, dont l'intérieur est divisé en deux chambres de refroidissement (44, 45), est prévue sous les compresseurs de premier et deuxième étages (5,6) et
       en ce qu'un échangeur de chaleur (47) pour un refroidisseur intermédiaire (29) refroidissant un fluide émis à partir du compresseur de premier étage (5) et introduisant ensuite le fluide dans le compresseur de deuxième étage (6) est prévu à l'intérieur d'une des chambres de refroidissement (44), alors qu'un échangeur de chaleur (48) pour un refroidisseur final (33) refroidissant le fluide émis à partir du compresseur de deuxième étage (6) et rebutant ensuite le fluide est prévu à l'intérieur de l'autre chambre de refroidissement (45).
  4. Turbocompresseur selon la revendication 3, caractérisé en ce que chacune des chambres de refroidissement (44, 45) dans laquelle un fluide est introduit à partir des premier et deuxième compresseurs (5, 6) présente sensiblement une forme de parallélépipède rectangle, et en ce que chaque échangeur de chaleur (47, 48) est formé le long de la chambre de refroidissement associée (44, 45) de façon à présenter une forme allongée longitudinalement, et est situé dans le milieu de la chambre de refroidissement associée (44, 45) définissant une chambre d'entrée (49) et une chambre de sortie (50) par référence au sens de l'écoulement, et qu'une entrée d'air (51) avec une forme allongée est formée le long de chaque échangeur de chaleur (47, 48) au niveau d'une extrémité longitudinale de la chambre d'entrée (49), alors qu'une sortie d'air (52) est formée au niveau de l'extrémité diagonalement opposée de la chambre de sortie (50).
  5. Turbocompresseur selon la revendication 2, caractérisé en ce qu'une partie de fenêtre (149), destinée à exposer un accouplement d'arbre qui relie l'arbre de sortie (102) du moteur d'entraínement (100) et l'arbre d'entrée (114) de la boíte à engrenages (103), est formée dans le carter (110) de telle façon que la partie de fenêtre (149) soit située dans une partie de carter (110a) de boíte à engrenages qui reçoit la boíte à engrenages (103).
EP95115153A 1994-09-28 1995-09-26 Turbo-compresseur Expired - Lifetime EP0704624B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP233882/94 1994-09-28
JP23388294A JP3470410B2 (ja) 1994-09-28 1994-09-28 ターボ圧縮機
JP23388294 1994-09-28
JP23546294A JP3385745B2 (ja) 1994-09-29 1994-09-29 ターボ圧縮機
JP23546294 1994-09-29
JP235462/94 1994-09-29

Publications (2)

Publication Number Publication Date
EP0704624A1 EP0704624A1 (fr) 1996-04-03
EP0704624B1 true EP0704624B1 (fr) 2003-01-08

Family

ID=26531246

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95115153A Expired - Lifetime EP0704624B1 (fr) 1994-09-28 1995-09-26 Turbo-compresseur

Country Status (4)

Country Link
EP (1) EP0704624B1 (fr)
KR (1) KR100353889B1 (fr)
DE (1) DE69529321T2 (fr)
TW (1) TW291526B (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3799121B2 (ja) 1997-03-19 2006-07-19 株式会社 日立インダストリイズ ２段遠心圧縮機
JP4003378B2 (ja) * 2000-06-30 2007-11-07 株式会社日立プラントテクノロジー スクリュー圧縮機
JP2011220146A (ja) * 2010-04-06 2011-11-04 Ihi Corp ターボ圧縮機及びターボ冷凍機
JP7221727B2 (ja) * 2019-02-22 2023-02-14 三菱重工コンプレッサ株式会社 ギアド圧縮機の位相調整システム、ギアド圧縮機の位相調整治具、及びギアド圧縮機の位相調整方法
CN112901520A (zh) * 2021-03-30 2021-06-04 沈阳斯特机械制造有限公司 一种带进口导叶齿轮组装整体撬装式离心压缩机
CN115059629B (zh) * 2022-08-11 2022-11-01 中铁十八局集团泵业有限公司 一种基于惯性滑动型风机能效提升设备

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB714765A (fr) * 1900-01-01
US3476485A (en) * 1967-09-18 1969-11-04 Dresser Ind Multistage centrifugal compressor
US3717418A (en) * 1970-06-08 1973-02-20 Carrier Corp Compressor barrel assembly
US3658442A (en) * 1970-06-08 1972-04-25 Northern Research And Engineer Compressor
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
DE3513936C2 (de) * 1984-08-17 1986-12-04 Mannesmann AG, 4000 Düsseldorf Kühleinrichtung für einen mehrstufigen Verdichter

Also Published As

Publication number Publication date
DE69529321T2 (de) 2003-11-20
TW291526B (fr) 1996-11-21
KR100353889B1 (ko) 2003-02-05
KR960011149A (ko) 1996-04-20
DE69529321D1 (de) 2003-02-13
EP0704624A1 (fr) 1996-04-03

Similar Documents

Publication Publication Date Title
US6572350B2 (en) Screw compressor
US7967551B2 (en) Suction filter, turbocompressor, and method for compact assembling of the same
JPS5914605B2 (ja) 水冷式内燃機関用補助機器総合構成体
US8734126B2 (en) Screw compressor
US6010320A (en) Compressor system having an oil separator
US4174196A (en) Screw fluid machine
KR100871623B1 (ko) 패키지형 압축기
JP2007332826A (ja) 遠心圧縮機
JPS6138357B2 (fr)
EP0704624B1 (fr) Turbo-compresseur
US4302160A (en) Silently operating fluid pump unit
JP4048078B2 (ja) ターボ圧縮機
JP3470410B2 (ja) ターボ圧縮機
US6991440B2 (en) Two-stage screw compressor
JP2005171957A (ja) パッケージ型圧縮機
JP3480009B2 (ja) 遠心式圧縮機
JPS5848756B2 (ja) スクリユ−流体機械
JPH07133774A (ja) オイルフリースクリュー圧縮機
JP2002295383A (ja) スクリュ圧縮機
GB2088960A (en) Rotary Positive-displacement Gas Compressors
KR0165655B1 (ko) 콤프레서 시스템
JP3385745B2 (ja) ターボ圧縮機
CN101105191A (zh) 涡轮压缩机及其装配方法
US20230332603A1 (en) Package-type compressor
JP2512247B2 (ja) 無給油式回転形圧縮機ユニット装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB IT LI

AX Request for extension of the european patent

Free format text: LT;LV;SI

RAX Requested extension states of the european patent have changed

Free format text: LT;LV;SI

17P Request for examination filed

Effective date: 19960614

RBV Designated contracting states (corrected)

Designated state(s): CH DE FR GB IT LI

17Q First examination report despatched

Effective date: 20010705

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69529321

Country of ref document: DE

Date of ref document: 20030213

Kind code of ref document: P

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWAELTE FELDMANN & PARTNER AG

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20031009

REG Reference to a national code

Ref country code: CH

Ref legal event code: PFA

Owner name: ISHIKAWAJIMA-HARIMA HEAVY INDUSTRIES CO., LTD.

Free format text: ISHIKAWAJIMA-HARIMA HEAVY INDUSTRIES CO., LTD.#2-1, OHTEMACHI 1-CHOME#CHIYODA-KU, TOKYO (JP) -TRANSFER TO- ISHIKAWAJIMA-HARIMA HEAVY INDUSTRIES CO., LTD.#2-1, OHTEMACHI 1-CHOME#CHIYODA-KU, TOKYO (JP)

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140923

Year of fee payment: 20

Ref country code: CH

Payment date: 20140915

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140924

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20140917

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140906

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 69529321

Country of ref document: DE

Representative=s name: SCHAUMBURG & PARTNER PATENTANWAELTE GBR, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 69529321

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20150925

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20150925