GB2381960A - Refrigerant compressor and pressure-resistant vessel - Google Patents
Refrigerant compressor and pressure-resistant vessel Download PDFInfo
- Publication number
- GB2381960A GB2381960A GB0207135A GB0207135A GB2381960A GB 2381960 A GB2381960 A GB 2381960A GB 0207135 A GB0207135 A GB 0207135A GB 0207135 A GB0207135 A GB 0207135A GB 2381960 A GB2381960 A GB 2381960A
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- United Kingdom
- Prior art keywords
- electric motor
- closed vessel
- pressure
- motor unit
- refrigerant
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/20—Manufacture essentially without removing material
- F04C2230/23—Manufacture essentially without removing material by permanently joining parts together
- F04C2230/231—Manufacture essentially without removing material by permanently joining parts together by welding
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/803—Electric connectors or cables; Fittings therefor
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Motor Or Generator Frames (AREA)
Abstract
In a prior-art refrigerant compressor, a three-phase integral-type sealed terminal, in which three pins connected to a three-phase power source are disposed on one metal base portion, is attached to a body portion 10d of a closed vessel 10, for supplying electric power to an electric motor 7. When a high hydrostatic pressure load is applied to the closed vessel, it is deformed into a barrel shape, and the sealed terminal pulled in the circumferential direction owing to the deformation of the closed vessel is deformed elliptically. There may arise a problem with a glass material for insulating the metal base portion from the pins. To solve the problem, three small-diameter sealed phase terminals 6 independent of one another are disposed in the body portion 10d of the closed vessel 10, for supplying electric power to the electric motor unit 7. The terminals 6 are arranged substantially in a line in the circumferential direction of the body portion 10d of the closed vessel, or in a triangular arrangement. Pipes 3,4 are attached to respective holes 10b,c with a burred portion 12.
Description
-'- 2381960
REFRIGERANT COMPRESSOR AND PRESSURE-RESISTANT VESSEL
Field of the Invention
The present invention relates to a closed vessel for a refrigerant compressor and a pressure-resistant vessel, and particularly relates to the improvement of the pressure-resistant strength of a closed vessel for a refrigerant compressor and the improvement of the pressure-resistant strength of a pressure-resistant vessel.
Background of the Invention
Fig. 7 shows a scroll compressor as an example of a prior-art refrigerant compressor.
In Fig. 7, a closed vessel 10 is constituted by a cylindrical body portion led, an upper end cover lee and a lower end cover lOf.
A compression mechanism unit 1 and an electric motor unit 7 are disposed in the closed vessel 10. Both the units are connected to each other through a drive shaft 8. In the compression mechanism unit 1, a lowpressure refrigerant gas taken in through a suction pipe 3 is compressed by use of rotation given from the electric motor unit 7 through the drive shafts. The refrigerant gas brought thus into a high pressure state is discharged into the closed vessel 10 through a discharge port If. The closed vessel 10 in which the
-2 electric motor unit 7 is disposed, is filled with the high pressure refrigerant gas so that a high pressure atmosphere is produced in theclosedvessellO. Thehighpressurerefrigerantgasisdischarged into a refrigerating cycle outside the closed vessel through a discharge pipe 4 disposed in the body portion led of the closed vessel 10. In addition, a sealed terminal 5 is disposed in the body portion led of the closed vessel 10. The electric motor unit 7 is supplied with electric power through the sealed terminal 5.
Figs. 8A and 8B are main portion sectional views showing the state where the sealed terminal is attached to the closed vessel.
Fig.8Aillustratesasectionviewedfrom asideofthesealedterminal 5. Fig. 8B illustrates a section viewed from the front likewise.
In Figs. 8A and 8B, the sealed terminal 5 has a structure in which three pins 5b are disposed on a circular metal base portion 5a, andtherespectivepinsandthemetalbaseportionareelectrically insulatedfromoneanotherbyglasssealingwithglass5c. The sealed terminals is electrically welded to en attachment hole lOa provided in the outer wall of the body portion led of the closed vessel 10.
The attachment hole lea has a diameter substantially equal to that ofthemetalbaseportion5a. Thus,the sealed terminals is designed to ensure the airtightness between the inside and outside of the closed vessel 10.
Next, description will be made about the attachment of the
suction pipe 3 and the discharge pipe 4 to the closed vessel 10.
Fig.9 is a main portion sectional view showing the state where ill IlQ.B! 18! 81 1 51 - 0181111 _ 1 ' 111 111 1 11 111 1 111
1, 3- the suction pipe 3 is attached to the closed vessel 10.
In Fig. 9, a joint pipe 3a is braze-welded and attached to an attachment hole lOb formed in the body portion led of the closed vessel 10. An outside pipe 3b is inserted into the inside of the joint pipe 3a up to a suction port la of the compression mechanism unit. Then, an inside pipe 3c is further attached to the inside of the outside pipe 3b by press fitting. The outer circumference of the outside pipe 3b is pressed and expanded by the press fitting of the inside pipe 3c so as to come into close contact with the inner circumference of the suction port la of the compression mechanism unit. Thus, the airtightness between the inside and outside of the closed vessel can be kept.
The suction pipe 3 is inserted into the outside pipe 3b, and braze-welded to the joint pipe 3a and the outside pipe 3b simultaneously. Thus, the suction pipe 3 is designed to keep the airtightness between the inside and outside of the closed vessel 10. Fig. 10 is a main portion sectional view showing the state where the discharge pipe 4 is attached to the closed vessel 10.
In Fig. 10, a joint pipe 4a is braze-welded to an attachment hole lOc formed in the body portion led of the closed vessel 10 in the same manner as the suction pipe 3. The discharge pipe 4 is inserted into the inside of the joint pipe 4a, and brazed thereto.
Thus, the discharge pipe 4 is designed to keep the airtightness between the inside and outside of the closed vessel 10.
1 1 - 4- In the prior-art refrigerant compressor,a three-phase power supply was attached to the body portion led of the closed vessel 10 in the form of the comparatively large-diameter sealed terminal 5disposedonthemetalbaseportion5a. Accordingly,whentheclosed vessel 10 was filled with a high pressure gas, particularly when the pressure in the closed vessel 10 increased to an abnormally high pressure for some reason, the sealed terminal attaching hole lea might be deformed elliptically. In the worst case, there might arise a trouble in the welded portion of the sealed terminal 5 due to the pressure stress.
In addition, when a high hydrostatic pressureload was applied to the closed vessel 10 in a hydrostatic pressure overload test forsecuringasafetystandard,therewasacasewhereagivenstandard pressure could not be cleared. That is, the closed vessel 10 was deformed into a barrel-like shape, and the sealed terminal 5 pulled in the circumferential direction accordingly with the deformation of the closed vessel 10 was deformed elliptically. Thus, the glass 5c for insulating the metal base portion 5a from the pins 5b was cracked and broken.
Figs. llA to llC show the circumstances in which the closed vesselandthesealedterminalaredeformedinahydrostaticpressure overload test. Fig. llA is an exterior view showing the deformation of the closed vessel. Fig. llB is a sectional view showing the deformation of the sealed terminal. Fig. llC is a view showing the deformationofthecircularmetalbaseportion. Withthebarrel-like _.' I. 's 's s ' 11. 111 R lllill C 11 1 1l 1l ll l8 - Ill 1 1l l Ill
deformation of the closed vessel 10, the sealed terminal attaching holelOa is also pulled in the circumferentialdirection end deformed elliptically. With the deformation of the sealed terminalattaching hole lea, the sealed terminal 5 is pulled accordingly and deformed elliptically. At the same time, the sealed terminal 5 suffers the hydrostatic pressure from the inside of the closed vessel 10 so as to be pushed outwardly. The glass Sc for insulating the metal base portion 5a from the pins 5b cannot accommodate the plastic deformation of the metal base portion 5a. Thus, the glass 5c is cracked end broker. In addition, when the deformation of the sealed terminal attaching hole lea is great, the close contact between the sealed terminal 5 and the electrically welded portion in the outer circumference of the sealed terminal 5 may be broken to cause destruction. In addition, in the prior-art refrigerant compressor, the suction pipe 3 and the discharge pipe 4 were attached to the body portion led of the closed vessel 10. Accordingly, when the closed vessel 10 was filled with a high pressure gas, particularly when the pressure in the closed vessel 10 increased to an abnormally high pressure for some reason, the attachment holes 10b and lOc for the respective joint pipes 3a and 4a of the suction pipe 3 and the discharge pipe 4 might be deformed elliptically. In the worst case, there might arise a problem in the welding due to the pressure I stress. In addition, in a hydrostatic pressure overload test for
-b- securing a safety standard, there was a case where a given standard pressure could not be cleared. That is, the closed vessel 10 was deformed into a barrel-like shape, and the joint pipe attaching holeslObandlOcpulledinthecircumferentialdirectionaccordingly with the deformation of the closed vessel 10 were deformed elliptically. Thus, the welded portions were cracked and broken.
Fig. 12 shows the attachment portion of the suction pipe 3 to the closed vessel lo subjected toe hydrostatic pressure overload test. With the barrel-like deformation of the closed vessel lo, the attachment hole lob for the suction pipe 3 is pulled accordingly in the circumferential direction so as to be deformed elliptically.
When the deformation further goes on, the welded portion between the outer circumference of the joint pipe 3a and the attachment holelObiscrackedandbroken. The circumstances when the discharge pipe is broken are similar to those in the case of the suction pipe in Fig. 12.
It would therefore be desirable to improve the pressure-resistant strength of a closed vessel in a refrigerant compressor of a so-called high pressure shell system.
It would also be desirable to improve the pressure-resistant strength of a sealed terminal attaching portion or portions of the closed vessel.
It would also be desirable to improve the _,,,,,._,, - At_ 81 I 11! 111 allllc llalll 11 1 111
-7- pressure-resistant strength of a suction pipe attaching portion and a discharge pipe attaching portion of the closed vessel.
It would also be desirable to improve the pressure-resistant strength of a pressure-resistant vessel.
It would also be desirable to improve the pressure-resistant strength of a sealed terminal attaching portion or portions of the pressure-resistant vessel.
It would also be desirable to improve the pressure-resistant strength of a pipe attaching portion or portions of the pressure-resistant vessel.
In the refrigerant compressor defined in Claim 1, three sealed
terminals for supplying electric power to an electric motor of an electricmotorunitareeachattachedtoaclosedvesselindependently of one another for every phase.
In the refrigerant compressor defined in Claim 2, the three phase terminals each attached to the closed vessel independently of one another for every phase are aligned substantially in a line inacircumferentialdirectionofabodyportionoftheclosedvessel. In the refrigerant compressor defined in Claim 3, at least one of a suction pipe for sucking a refrigerant and a discharge pipe for discharging the refrigerant after compression is attached to en attachment hole formed in en attachment hole formation portion of a closed vessel with a front end portion thereof subjected to burring. In the refrigerant compressor defined in Claim 4, three sealed
- - terminals for supplying electric power to an electric motor of an electricmotorunitareeachattachedtoaclosedvesselindependently of one another for every phase, while at least one of a suction pipe and a discharge pipe is attached to an attachment hole formed in an attachment hole formation portion of the closed vessel with a front end portion thereof subjected to burring.
In the refrigerant compressor defined in Claim 5, at least one sealed terminal for supplying electric power to an electric motor of an electric motor unit is attached to an attachment hole formed in an attachment hole formation portion of a closed vessel with a front end portion thereof subjected to burring. Either three sealedphaseterminalsorathreephaseintegraltypesealedterminal may be used.
The pressure-resistant vessel defined in Claim 6 is a pressure-resistant vessel for receiving an electric motor unit, wherein sealed terminals for supplying three-phase electric power to en electric motor unit are each attached to the pressure-resistant vessel independently of one another for every phase.
The pressure-resistant vessel defined in Claim 7 contains at leastoneofapipeforintroducingafluidintothepressure-resistant vesselandapipeforextractingthefluidfromthepressure-resistant vessel, the pipe being attached to an attachment hole formed in an attachment hole formation portion of the pressure-resistant vessel with a front end portion thereof subjected to burring.
_,.,,,,._., it,,, Ileeel il Fell 11'! IN IlI lIF,11 ' 51 Ill 1111 1! 111 1 1111 1l
-9- BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a longitudinal sectionalviewof a scroll compressor according to an embodiment of the invention; Figs. 2A to 2C are views for explaining the sealed terminals in the embodiment of the invention; Figs. 3A and 3B are a graph and a view explanatorily showing thebreakingstrengthsofclosedvesselstowhichthesealedterminal or terminals have been attached in a hydrostatic pressure overload test according to the embodiment of the invention; Fig. 4isanexplanatoryviewshowingthestatewherethesuction pipeisattachedLotheclosedvesselaccordingtothe embodiment of the invention; Fig, 5 is an explanatory view showing the state where the discharge pipe is attached to the closed vessel according to the embodiment of the invention; Fig. 6 is a graph explanatorily showing the breaking strengths of the closed vessels to which the suction pipe has been attached in a hydrostatic pressure overload test according to the embodiment of the invention; Fig. 7 is a longitudinal sectional view of a prior-art scroll compressor; Figs. 8A and 8B are main portion sectional views showing the state where the sealed terminal is attached to the closed vessel in the prior art;
Fig. 9 is a main portion sectionalview showing the state where _
- lo -
the suction pipe is attached to the closed vessel in the prior art;
Fig. 10 is a main portion sectional view showing the state where the discharge pipe is attached to the closed vessel in the prior art;
Figs. llA to llC are views showing the circumstances in which the closed vessel and the sealed terminal are deformed when a hydrostaticpressureoverloadtestwasconductedontheclosedvessel in the prior art; and
Fig.12is a view showing the attachment portion for the suction pipe when the hydrostatic pressure overload test was conducted on the closed vessel in the prior art.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Fig. 1 is alongitudinal sectional view of a scroll compressor as an example of a refrigerant compressor according to an embodiment of the invention.
In Fig. 1, a closed vessel 10 is constituted by a cylindrical body portion led, an upper end cover 10e and a lower end cover 10f.
A compression mechanism unit 1 and an electric motor unit 7 are received in the closed vessel 10. The compression mechanism unit 1 has a fixed scroll, a rocking scroll, and so on. The electric motor unit 7 has an electric motor constituted by a stator and a rotor. Both the units are connected to each other through a drive shaft 8. In the compression mechanism unit 1, a low-pressure ti'.: In, 11111 IRISH I ' 1 1 - 1 1!18!8 lIE 18
- 11 refrigerant gas taken in through a suction pipe 3 is compressed by use of the rotation given from the electric motor unit 7 through the drive shaft 8. The refrigerant gas brought thus into a high pressure state is discharged into the closed vessel 10 through a discharge port If. The closed vessel 10 in which the electric motor unit 7 is disposed, is filled with the high pressure refrigerant gas so that a high pressure atmosphere is produced in the closed vessel 10. This refrigerant gas is discharged into a refrigerating cycleoutsidetheclosedvessellOthroughadischargepipe4 disposed in the body portion led of the closed vessel 10.
Three small-diameter sealed terminals 6 (one of them is shown in Fig. 1) are disposed in the body portion led of the closed vessel 10. The electric motor unit 7 is supplied with three-phase electric power through the sealed terminals 6.
In addition, attachment hole formation portions in the outer wall of the closed vessel 10 to which the suction pipe 3 and the discharge pipe 4 are attached are subjected to burring (each burred or deburred portion is specified by the reference numeral 12 in Fig. 1). Each of the attachment hole formation portions is thicker than any other outer wall portion.
The other constituent members are similar to those of Fig. 7 for the prior art, and referenced correspondingly. Description
of those constituent members will be therefore omitted.
Figs. 2A to 2C are views for explaining the sealed terminals in the first embodiment of the invention. Fig. 2A is a sectional
-12 view of the sealed terminal. Fig. 2B is a schematic layout view showingthepinsofthesealedterminalsalignedinasingletransverse line. Fig. 2C is a schematic layout view showing the pins of the sealed terminals located in angular positions.
InFigs.2Ato2C,as the sealed terminals6 in this embodiment, three phase terminals 6 each having a smaller diameter than the three-phase integral type sealed terminal 5 in the prior art,are
disposed in the closed vessel 10.
Each phase terminal 6 has a structure in which a single pin 6b connected to one of the three phases of a power supply is disposed on a smalldiameter circular metal base portion 6a, and the pin 6b and the metal base portion 6a are electrically insulated from each other by glass sealing with glass 6c. The phase terminal 6 is electrically welded to an attachment hole lea provided in the outer wall of the body portion led of the closed vessel 10. The attachment hole lea has a diameter substantially equal to that of the metal base portion 6a. Thus, the phase terminal 6 is designed to ensure the airtightness between the inside and outside of the closed vessel 10.
As for the method of arranging the three phase terminals 6, the phase terminals 6 may be aligned in a line in the circumferential direction of the closed vessel 10 as shown in Fig. 2B, or located in the angular positions of an equilateral triangle as shown in Fig. 2C.
Each sealed terminal 6 (phase terminal 6) is arranged to have ,, be_ _ la _ 15- 1 1 1 1111- 111 1 1 111511 11111 1 11-S e 11 1 1 11111111118
-13- a small diameter in such a manner. Thus, the terminal attaching hole lea can be restrained from being deformed elliptically due tothebarrellikedeformationoftheclosedvessellO. In addition, since the sealed terminal 6 itself becomes smaller, its rigidity increases. Thus,the sealed terminal 6 is restrained from swelling out due to the internal pressure, so that the stress of the metal base portion 6a end the pin 6b on the insulating glass 6c is reduced.
As a result, both the pressure-resistant strength of the sealed terminals and the pressure-resistant strength of the attachment portions involved in the phase terminals 6 increase so as to lead to the improvement of the pressure-resistant strength of the closed vessel 10 as a whole.
Fig. 3A shows the breaking strength of the closed vessel 10 in a hydrostatic pressure overload test conducted when such sealed terminals 6 have been attached (the hydrostatic pressure overload test conductedina condition that no load was applied to the suction pipe attaching portion and the discharge pipe attaching portion).
Fig. 3A shows, in comparison, the breaking strength in the case of the three-phase integral type sealed terminal 5 in the prior art, the breaking strength in the case of the three phase terminals 6 aligned in a single transverse line, and the breaking strength in the case of the three phase terminals 6 located in the angular positions of an equilateral triangle.
While the breaking strength in the case of the three-phase integral type sealed terminal 5 in the prior art was 18 MPa in
-14- hydrostaticpressure,thebreakingstrength in the ease of the sealed terminals 6 in this embodiment was 25 MPa. Thus, a strength improvement of about 40% could be obtained. On the other hand, as for the manner to arrange the phase terminals 6, the pressure-resistant strength in the ease of the three phase terminals 6 aligned in a line in the circumferential direction was 25 MPa while the pressure-resistant strength in the ease of the three phase terminals 6 located in the angular positions of an equilateral triangle was 22 MPa, which was lower than 25 MPa in the former case.
In this breaking in the case of the three phase terminals 6 located in the angular positions, a crack ll was produced between the terminal attaching holes lea different in axial height as shown in Fig. 3B. This fact suggests that the attachment holes 10a are preferably attached horizontally in the circumferentialdirection.
However, even in the case of the three phase terminals 6 located in the angular positions, the strength increases in comparison with the case of the three-phase integral type sealed terminal 5 in the prior art.
Incidentally, the manner to arrange the three phase terminals 6 in the closed vessel is not limited to the above-mentioned two arrangement cases. An excellent result can be obtained when the three phase terminals6 are arranged conveniently for the connection to a three-phase power supply, and at a balanced distance, that is, at a distance not too close to one another and not too far from one another for the purpose of securing the strength.
r l,'' Ile,..,,l,,,' ls IleIlIs_! ' i:l.i 11. 1
-15 Figs. 4 and 5 are explanatory views showing the states where the suction pipe and the discharge pipe are attached to the body portion led of the closed vessel lo in Fig. l, respectively.
In Figs. 4 and 5, the attachment hole formation portions for forming the attachment holes lOb and lOc in the closed vessel lo havetheirfrontendportionssubjectedtoburringsoastobeportions for attaching joint pipes 3a and 4a for the suction pipe 3 and the discharge pipe 4 to the closed vessel lo (each burred portion is specified by the reference numeral 12 in Figs.4and5),thus forming the attachment holes lob and lOc.
Since the burring is performed, the vicinities (attachment hole formation portions) of the attachment holes lob and lOc for the joint pipes 3a and 4a can be made thicker than any other outer wallportionoftheclosedvessel. Accordingly,the attachment holes lob and lOc can be restrained from being deformed elliptically due to the barrel-like deformation of theclosedvessellO. The welding with the joint pipes 3a and 4a can be also restrained from cracking.
Thus, the burring is useful in improving the pressure-resistant strength of the closed vessel lo.
Incidentally, when the attachment hole front end portions are bentoutwardsoastoincreasethethicknessinthefrontendportions, and the suction pipe 3 and the discharge pipe 4 are then attached thereto, the effects substantially similar to those in the case of the burring can be obtained.
Fig. 6 shows the comparison in the hydrostatic pressure
-1 overload test results (the hydrostatic pressure overload test conducted in a condition no load was applied to the sealed terminal attaching portion(s) and the discharge pipe attaching portion) between the pressure-resistant strength of the closed vessel lO in which the suction pipe 3 was attached to the attachment hole lob subjected to burring and the pressure-resistant strength of the prior-art closed vessel lO subjected to no burring.
Because the attachment hole lOb for the joint pipe 3a was improved in strength by the burring so as to be restrained from being deformed elliptically, the pressure-resistant strength in this embodiment was 25 MPa in hydrostatic pressure while that in the prior art was 20 MPa likewise. Thus, a pressure-resistant
strength improvement of about 25% could be obtained.
As for the discharge pipe 4, the similar results of the hydrostatic pressure overload test could be obtained.
Incidentally,because the attachment hole formation portions are increased in thickness by the burring, sufficient pressure-resistant strength can be obtained even if the suction pipe 3 and the discharge pipe 4 are attached to the attachment holes lOb and lOc directly without interposition of the joint pipes 3a and 4a, respectively.
The above embodiment has described en example where the sealed terminals 6 were attached, as small-diameter phase terminals, to the attachment holes lea. In the same manner as the case for the suction pipe 3 and the discharge pipe 4, the sealed terminals 6 'I', sie'si' ' 1 1 1i 11 1- 11 c' 1:! 18 11! 11! 111!111!
-17 may be attached to the attachment holes lOa of the closed vessel lO subjected to burring so that the pressure-resistant strength of the closed vessel lo can be improved.
In this case, it is most preferable that the sealed terminals are formed as phase terminals. However, even if the prior-art three-phase integral type sealed terminal 5 is used, the attachment hole lea can be restrained from being deformed elliptically due to the barrel-like deformation of the closed vessel lO. Thus, the pressure-resistant strength of the closed vessel lo is improved in comparison with the prior-art example.
Incidentally, a closed vessel to most excellent in pressure-resistant strength can be obtained by carrying out the following three, that is, the structure concerning the sealed terminals 6 and the method of attaching the sealed terminals 6 to the closed vessel lo according to the invention, the method of attaching the suction pipe 3 to the closed vessel lo according to the invention, and the method of attaching the discharge pipe 4 to the closed vessel lo according to the invention. However, when any one or two of the three are carried out, a closed vessel lO improved in pressure-resistant strength can be obtained.
In addition, the structure concerning the sealed terminals 6 and the method of attaching the sealed terminals 6 to the closed vessel lO according to the invention, the method of attaching the suction pipe 3 to the closed vessel to according to the invention, and the method of attaching the discharge piped to the closed vessel
- 16-
10 according to the invention, can be applied broadly not only to scroll compressors but also to other high pressure shell type compressors such as rotary compressors or screw compressors.
Further, the structure concerning the sealed terminals 6 and the method of attaching the sealed terminals 6 to the closed vessel 10 according to the invention, the method of attaching the suction pipe 3 to the closed vessel 10 according to the invention, and the method of attaching the discharge pipe 4 to the closed vessel 10 according to the invention, can be applied broadly to pressure-resistant vessels in the same manner as the closed vessel 10 for a compressor.
That is, sealed terminals for supplying three-phase electric power to an electric motor unit in a pressure-resistant vessel receiving the electric motor unit may be attached to the pressure-resistant vessel independently of one another, one for each phase. Thus, the strength of the pressureresistant vessel and the strength of the attachment portions can be improved.
Further, in a pressure-resistant vessel having at least one of a pipe for introducing a fluid into the pressure-resistant vessel and a pipe for extracting the fluid from the pressure-resistant vessel, the pipe may be attached to an attachment hole formed in en attachment hole formation portion with a front end portion thereof subjected to burring. Thus, the strength of the pressure-resistant vessel and the strength of the attachment portion can be improved.
As described above, in the refrigerant compressor according _,,,,,,,,,,,'. ilIll,' 'l_e 1_ 1118_ 1111 Ill.'rllF 11 Fill
-19 - to Claim 1 of the invention, three sealed terminals for supplying electric power to an electric motor of an electric motor unit are each attached to a closed vessel independently of one another for every phase.
Accordingly, the diameters of sealed terminalattaching holes aresmall, sothatthe strength against the deformation of the sealed terminals themselves is improved and the elliptic deformation of the sealed terminal attaching holes due to the barrel-like deformation of the closed vessel can be restrained to a minimum.
Thus, an improvement is achieved in the strength of the sealed terminals, the strength of the attachment portions,andthestrength of the closed vessel having the attachment portions to which the sealed terminals are attached. It is therefore possible to obtain a refrigerant compressor excellent in pressure-resistant strength and high in reliability.
Further, in the refrigerant compressor defined in Claim 2, the three phase terminals each attached to the closed vessel independently of one another for every phase are aligned substantially in a line in a circumferentialdirection of a body portion of the closed vessel.
Accordingly, cracking among the attachment holes can be restrained to a minimum. It is therefore possible to obtain a refrigerant compressor with sealed terminals and a closed vessel more excellent in pressure-resistant strength and higher in reliability.
- 20V In the refrigerant compressor defined in Claim 3, at least one of a suction pipe for sucking a refrigerant and a discharge pipe for discharging the refrigerant after compression is attached to an attachment hole formed in en attachment hole formation portion of a closed vessel with a front end portion thereof subjected to burring. Accordingly, the strength of the attachment portion of the attachment hole is improved so that the elliptic deformation of the attachment portion of the attachment hole due to the barrel-like deformation of the closed vesselcanbe restrained. It is therefore possible to obtain a closed vesselwitha suction pipe end a discharge pipe excellent in pressure-resistant strength and high in reliability, and hence to obtain a refrigerant compressor high in reliability. In the refrigerant compressor defined inClaim4,three sealed terminals for supplying electric power to an electric motor of an electricmotorunitareeachattachedtoaclosedvesselindependently of one another for every phase, while at least one of a suction pipe and a discharge pipe is attached to an attachment hole formed in an attachment hole formation portion of the closed vessel with a front end portion thereof subjected to burring.
Accordingly, it is possible to obtain a closed vessel with sealed terminals, a suction pipe and a discharge pipe excellent in pressureresistant strength, and hence to obtain a refrigerant compressor high in reliability.
_.,,., i,, i','' '. ' Il DING 11111 1 ' 1!!111!e 11r1! I E! 11 Dial
-21 In the refrigerant compressor defined in Claim 5, at least one sealed terminal for supplying electric power to an electric motor of an electric motor unit is attached to an attachment hole formed in an attachment hole formation portion of a closed vessel with a front end portion thereof subjected to burring.
Accordingly, the strength of the attachment portion of the attachment hole is improved so that the elliptic deformation of the attachment portion of the attachment hole due to the barrel-like deformation of the closed vesselcanbe restrained. It is therefore possible to obtain a closed vessel with at least one sealed terminal excellent in pressure- resistant strength, and hence to obtain a refrigerant compressor high in reliability.
The pressure-resistant vessel defined in Claim 6 is a pressure-resistant vessel for receiving an electric motor unit, wherein sealed terminals for supplying three-phase electric power totheelectricmotorunitareeachattachedtothepressure-resistant vessel independently of one another for every phase. Accordingly, the strength of the pressure-resistant vessel and the strength of the attachment portion can be improved.
The pressure-resistant vessel defined in Claim 7 contains at leastoneofapipeforintroducingafluidintothepressure-resistant vesselandapipeforextractingthefluidfromthepressure-resistant vessel, the pipe being attached to an attachment hole formed in an attachment hole formation portion of the pressure-resistant vessel with a front end portion thereof subjected to burring.
-22 Accordingly, the strength of the pressure-resistant vessel and the strength of the attachment portion can be improved.
,,,,,,,.; [ Act_ 1 1 11 1 1 1 1111511 I! it -! 111 ', 1 1 1 1 I,
Claims (7)
1. A refrigerant compressor of a high pressure shell system . comprising: a compression mechanism unit for compressing a refrigerant; an electric motor unit; a drive shaft for transmitting driving power of said electric motor unit to said compression mechanism unit; and a closed vesselforreceivingsaidcompressionmechanismunit, said electric motor unit and said drive shaft, a high pressure atmosphere being produced in said closed vessel by said compressed refrigerant; wherein three sealed terminals for supplying electric power to an electric motor of said electric motor unit are each attached to said closed vessel independently of one another for every phase.
2. A refrigerant compressor according to Claim 1, wherein said three phase terminals each attached to said closed vessel independently of one another for every phase are aligned substantially in a line in a circumferential direction of a body portion of said closed vessel.
3. A refrigerant compressor of a high pressure shell system comprising: a compression mechanism unit for compressing a refrigerant;
-24 an electric motor unit; a drive shaft for transmitting driving power of said electric motor unit to said compression mechanism unit; and aclosedvesselforreceivingsaidcompressionmechanismunit, said electric motor unit and said drive shaft, a high pressure atmosphere being produced in said closed vessel by said compressed refrigerant; wherein at least one of a suction pipe for sucking said refrigerant and a discharge pipe for discharging said refrigerant after compression is attached to an attachment hole formed in an attachment hole formation portion of said closed vessel with a front end portion thereof subjected to burring.
4. A refrigerant compressor of a high pressure shell system comprising: a compression mechanism unit for compressing a refrigerant; an electric motor unit; a drive shaft for transmitting driving power of said electric motor unit to said compression mechanism unit; and aclosedvesselforreceivingsaidcompressionmechanismunit, said electric motor unit and said drive shaft, a high pressure atmosphere being produced in said closed vessel by said compressed refrigerant; wherein three sealed terminals for supplying electric power to an electric motor of said electric motor unit are each attached _, _ _.,,'',.-_. I''.',' '' '.' ''' 111_11 11111114 18 11 1111 1111111' 1111 111
!. -25
to said closed vessel independently of one another for every phase, while at least one of a suction pipe for sucking said refrigerant and a discharge pipe for discharging said refrigerant after compressionis attached to en attachment hole formed in en attachment hole formation portion ofeaid closed vessel with a front end portion thereof subjected to burring.
5. A refrigerant compressor of a high-pressure shell system comprising: a compression mechanism unit for compressing a refrigerant; an electric motor unit; a drive shaft for transmitting driving power of said electric motor unit to said compression mechanism unit; and a closed vessel for receiving said compression mechanism unit, said electric motor unit and said drive shaft, a high pressure atmosphere being produced in said closed vessel by said compressed refrigerant; wherein at least one sealed terminal for supplying electric power to an electric motor of said electric motor unit is attached to en attachment hole formed in en attachment hole formation portion of said closed vessel with a front end portion thereof subjected to burring.
6. A pressure-resistant vessel for receiving an electric motor unit, comprising:
sealed terminals for supplying three-phase electric power to said electric motor unit, said sealed terminals being attached to said pressure-resistant vessel independently of one another, each for every phase.
7. A pressure-resistant vessel substantially as described with reference to Figure 1, 2A, and 2B of the accompanying drawings.
7. A pressure-resistant vessel comprising: at least one of a pipe for introducing a fluid into said pressure-resistant vessel and a pipe for extracting said fluid from said pressure-resistant vessel, said pipe being attached to an attachment hole formed in an attachment hole formation portion of said pressure-resistant vessel with a front end portion thereof subjected to burring.
_.,,._. _,... __, _. 1111 1 1 _11 1 1111 1 15111 B 151 11_ 81 11 11: 111' 1 1 11 11 15
8. A refrigerant compressor substantially as described with reference to, and as shown in, Figures 1 to 5 of the accompanying drawings.
9. A pressure-resistant vessel comprising a pipe for introducing or extracting a fluid, substantially as described with reference to Figure 1 and Figure(s) 4 and/or 5 of the accompanying drawings.
1+ Amendments to the claims have been filed as follows Claims: 1. A refrigerant compressor of a high pressure shell system, comprising: a compression mechanism unit for compressing a refrigerant; an electric motor unit; a drive shaft for transmitting driving power of the electric motor unit to the compression mechanism unit; and a closed vessel for receiving the compression mechanism unit, the electric motor unit, and the drive shaft, a high pressure atmosphere being produced in the closed vessel by the compressed refrigerant; wherein three single sealed terminals for supplying three-phase electric power to an electric motor of the electric motor unit are each attached to a body portion of the closed vessel independently of one another, there being a single sealed terminal for each phase; and wherein the three terminals are aligned substantially in a line in a circumferential direction of the body portion of the closed vessel.
2. A refrigerant compressor as claimed in claim 1, wherein at least one of a suction pipe for sucking the refrigerant and a discharge pipe for discharging the refrigerant after compression is attached to an attachment hole formed in an attachment hole formation portion of the closed vessel with a front end portion thereof subjected to burring. 3. A refrigerant compressor as claimed in claim 1 or 2, wherein at least one of the three single sealed terminals ...-,. t, I-' F' ' T I fI'Illi lll ' III I 111::1 1! lll Illll el I
- 2% is attached to an attachment hole formed in an attachment hole formation portion of the closed vessel with a front end portion thereof subjected to burring.
4. A pressure-resistant vessel for receiving an electric motor unit, including: three single sealed terminals for supplying three-
phase electric power to the electric motor unit, the terminals being attached to a body portion of the pressure-
resistant vessel independently of one another, there being a single sealed terminal for each phase; wherein the three terminals are aligned substantially in a line in a circumferential direction of the body portion of the pressure-resistant vessel.
5. A pressure-resistant vessel as claimed in claim 4, wherein at least one of a pipe for introducing fluid into the pressure-resistant vessel and a pipe for extracting fluid from the pressure-resistant vessel is attached to an attachment hole formed in an attachment hole formation portion of the pressure-resistant vessel with a front end portion thereof subjected to burring.
6. A refrigerant compressor substantially as described with reference to, and as shown in, Figure 1, 2A, and 2B of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001344242A JP2003148344A (en) | 2001-11-09 | 2001-11-09 | Refrigerant compressor and pressure vessel |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB0207135D0 GB0207135D0 (en) | 2002-05-08 |
| GB2381960A true GB2381960A (en) | 2003-05-14 |
| GB2381960B GB2381960B (en) | 2004-02-04 |
Family
ID=19157797
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB0207135A Expired - Fee Related GB2381960B (en) | 2001-11-09 | 2002-03-26 | Refrigerant compressor and pressure-resistant vessel |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20030091446A1 (en) |
| JP (1) | JP2003148344A (en) |
| CN (1) | CN1228584C (en) |
| GB (1) | GB2381960B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1846658A1 (en) * | 2005-02-07 | 2007-10-24 | Carrier Corporation | Compressor terminal plate |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3954376B2 (en) * | 2001-12-25 | 2007-08-08 | 愛三工業株式会社 | Fuel pump |
| JP5762009B2 (en) * | 2011-01-19 | 2015-08-12 | 三菱電機株式会社 | Rotating electric machine |
| JP6370677B2 (en) * | 2014-10-28 | 2018-08-08 | 株式会社ヴァレオジャパン | Electric compressor |
| WO2016157236A1 (en) * | 2015-03-27 | 2016-10-06 | 三菱電機株式会社 | Fluid machine |
| CN106329790B (en) * | 2015-06-16 | 2018-12-25 | 佛山市建准电子有限公司 | Motor |
| US12046971B2 (en) | 2019-06-27 | 2024-07-23 | Mitsubishi Electric Corporation | Electric driving device and electric power steering device |
| CN112039267A (en) * | 2020-08-12 | 2020-12-04 | 西安中车永电捷力风能有限公司 | Terminal box for conductive bar and high-voltage double-fed wind driven generator and installation method thereof |
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| WO1994009541A1 (en) * | 1992-10-09 | 1994-04-28 | Mkm Magyar Kábel Muvek Résvénytársaság | Arrangement for disconnectable leading out and earthing of a metallic shield of a cable |
| JPH08109889A (en) * | 1994-10-12 | 1996-04-30 | Mitsubishi Heavy Ind Ltd | Scroll type compressor |
| EP1020646A1 (en) * | 1997-06-18 | 2000-07-19 | Matsushita Electric Industrial Co., Ltd. | Sealed type compressor |
| EP1045504A2 (en) * | 1999-04-12 | 2000-10-18 | Matsushita Electric Industrial Co., Ltd. | Motor-driven compressor |
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| JPS6179879A (en) * | 1984-09-27 | 1986-04-23 | Toshiba Corp | Compressor |
| US4800732A (en) * | 1988-04-28 | 1989-01-31 | American Standard Inc. | Refrigeration compressor with dual voltage hookup |
| US6102677A (en) * | 1997-10-21 | 2000-08-15 | Matsushita Electric Industrial Co., Ltd. | Hermetic compressor |
| JPH11303744A (en) * | 1998-04-20 | 1999-11-02 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| US6028523A (en) * | 1998-06-25 | 2000-02-22 | Carrier Corporation | Integral ground pin for sealed compressor |
| JP2000027757A (en) * | 1998-07-07 | 2000-01-25 | Sanyo Electric Co Ltd | Hermetic terminal for compressor |
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2001
- 2001-11-09 JP JP2001344242A patent/JP2003148344A/en active Pending
-
2002
- 2002-03-26 GB GB0207135A patent/GB2381960B/en not_active Expired - Fee Related
- 2002-04-09 US US10/118,253 patent/US20030091446A1/en not_active Abandoned
- 2002-06-28 CN CN02140205.1A patent/CN1228584C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994009541A1 (en) * | 1992-10-09 | 1994-04-28 | Mkm Magyar Kábel Muvek Résvénytársaság | Arrangement for disconnectable leading out and earthing of a metallic shield of a cable |
| JPH08109889A (en) * | 1994-10-12 | 1996-04-30 | Mitsubishi Heavy Ind Ltd | Scroll type compressor |
| EP1020646A1 (en) * | 1997-06-18 | 2000-07-19 | Matsushita Electric Industrial Co., Ltd. | Sealed type compressor |
| EP1045504A2 (en) * | 1999-04-12 | 2000-10-18 | Matsushita Electric Industrial Co., Ltd. | Motor-driven compressor |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1846658A1 (en) * | 2005-02-07 | 2007-10-24 | Carrier Corporation | Compressor terminal plate |
| EP1846658A4 (en) * | 2005-02-07 | 2008-08-20 | Carrier Corp | Compressor terminal plate |
| AU2005327257B2 (en) * | 2005-02-07 | 2011-05-12 | Carrier Corporation | Compressor terminal plate |
| US8317494B2 (en) | 2005-02-07 | 2012-11-27 | Carrier Corporation | Compressor terminal plate |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2381960B (en) | 2004-02-04 |
| JP2003148344A (en) | 2003-05-21 |
| CN1417475A (en) | 2003-05-14 |
| GB0207135D0 (en) | 2002-05-08 |
| CN1228584C (en) | 2005-11-23 |
| US20030091446A1 (en) | 2003-05-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 746 | Register noted 'licences of right' (sect. 46/1977) |
Effective date: 20100615 |
|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20160326 |