EP1319838B1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
EP1319838B1
EP1319838B1 EP03006364A EP03006364A EP1319838B1 EP 1319838 B1 EP1319838 B1 EP 1319838B1 EP 03006364 A EP03006364 A EP 03006364A EP 03006364 A EP03006364 A EP 03006364A EP 1319838 B1 EP1319838 B1 EP 1319838B1
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EP
European Patent Office
Prior art keywords
lubricant
oil
scroll
hermetic housing
rotating shaft
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
EP03006364A
Other languages
German (de)
French (fr)
Other versions
EP1319838A1 (en
Inventor
Toshihiko Mitsunaga
Kenzo Matsumoto
Kazuyoshi Sugimoto
Takahiro Nishikawa
Kazuaki Fujiwara
Kazuya Sato
Takashi Sato
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.)
Sanyo Electric Co Ltd
Original Assignee
Sanyo Electric Co Ltd
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Filing date
Publication date
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Priority claimed from EP98117556A external-priority patent/EP0903499B1/en
Publication of EP1319838A1 publication Critical patent/EP1319838A1/en
Application granted granted Critical
Publication of EP1319838B1 publication Critical patent/EP1319838B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/021—Control systems for the circulation of the lubricant

Definitions

  • the present invention relates to a scroll compressor mounted on an air conditioner, a refrigerating machine, etc. and, more particularly, to a scroll compressor adapted to discharge compressed gas, which has been compressed in a plurality of compression chambers formed by the engagement between a stationary scroll and a swivel scroll, out of a hermetic housing.
  • a scroll compressor employed for a refrigerating cycle of an air conditioner or the like is constructed as shown in Fig 4 as disclosed, for example, in Japanese Examined Patent Publication No. 7-99150.
  • a cylindrical hermetic housing 101 with its both ends closed includes an electric element 102 and a scroll compression element 103 therein.
  • the electric element 102 is composed of a stator 104 secured to the inner wall surface of the hermetic housing 101 and a rotor 105 rotatably supported in the stator 104, a rotating shaft 106 being connected to the rotor 105 in a penetrating fashion.
  • One end of the rotating shaft 106 is rotatably supported on a support frame 107 partly constituting the scroll compression element 103.
  • the other end of the rotating shaft 106 juts out of the rotor 105, a displacement pump 108 such as a trochoid pump, rotary pump, or reciprocating pump being connected to the distal end thereof.
  • An oil inlet pipe 109 is connected to an end of the displacement pump 108.
  • the end of the intake side of the oil inlet pipe 109 is extended downward so that it is submerged in a lubricant "b" contained in the hermetic
  • An oil feed passage for taking in the lubricant "b" by the displacement pump 108 is bored in the rotating shaft 106 in the axial direction, so that the lubricant is recirculated after it is supplied to sliding parts such as the support frame 107.
  • the central part of one end of the rotating shaft 106 supported by the support frame 107 in the penetrating manner is formed as a pin or crank 110 provided eccentrically in relation to the axial center of the rotating shaft 106.
  • a swivel scroll 111 is connected to the pin 110.
  • the swivel scroll 111 is formed into a discoid shape, a boss hole 112 for connection with the pin 110 being formed at the center of one side surface thereof, while a spiral lap 113 is integrally formed on the other side surface of the swivel scroll 111.
  • the stationary scroll 114 Joined to the support frame 107 is a stationary scroll 114.
  • the stationary scroll 114 has a spiral lap 115 formed on a portion thereof opposed to the swivel scroll 111, and also a plurality of compression chambers 116 formed between itself and the lap 113. These compression chambers 116 such in a refrigerant gas through the outer peripheral portion thereof and reduces the volumes as they move toward the center so as to compress the refrigerant gas.
  • a discharge port 117 is formed at the center of the stationary scroll 114.
  • the stationary scroll 114 is provided with a muffler 118 that surrounds the outer side of the discharge port 117.
  • a lubricant is sucked up and passed through the oil feed passage provided in the rotating shaft to be supplied to respective sliding parts including a support frame.
  • the swivel scroll is pressed against a stationary scroll by the foregoing pressure to bring them into contact so as to provide gas seal thereby to compress the refrigerant gas.
  • JP 06 058270 A and JP 06 058273A disclose a scroll compressor which is constituted so that oil is not injected into a compressor element at the time of a high circulating quantity of gas fluid, but oil is injected only at the time of a low circulating quantity.
  • a separate oil injection mechanism having a particular composition is installed in a particular position in the scroll compression element. Accordingly, it is an object of the present invention to provide a highly reliable scroll compressor with an improved oil injection mechanism.
  • a highly reliable scroll compressor equipped with an oil injection mechanism having a simple constitution in accordance with one aspect of the present invention is provided. This scroll compressor makes it possible to easily avoid insufficient supply of the lubricant to the compression chambers even when the number of revolutions of the rotary shaft decreases.
  • a scroll compressor according to Claim 1 of the present invention is equipped with an electric element and a scroll compression element driven by a rotating shaft of the electric element that are placed in a hermetic housing, a lubricant contained in the hermetic housing, and a lubricating portion provided on an end of the rotating shaft to supply the lubricant from the lubricating portion to respective sliding portions via an oil feed passage provided in the rotating shaft and to circulate it for reuse, wherein: an oil injection mechanism composed of an oil nozzle for injecting oil and a valve for opening/closing an oil feed passage inlet of the oil nozzle by the elasticity of a spring is provided in the vicinity of the position where a refrigerant gas is sucked into the scroll compression element from outside the hermetic housing, so that the valve opens the oil feed passage inlet to inject the lubricant held in the hermetic housing into the scroll compression element if the difference between the pressure in the hermetic housing that acts on the rear surface of the valve and the pressure in the vicinity of the position, where the
  • the injection amount of the lubricant is 0.1 to 3% for the elimination volume per unit time in the scroll compressor described in Claim 1.
  • the valve opens the oil feed passage inlet to inject the lubricant if the pressure differential is less than the range of 4x10 5 to 8x10 5 N/m 2 (4 to 8 kgf/cm 2 ) in the scroll compressor described in Claims 1 or 2.
  • the lubrication system in the lubricating portion in the scroll compressor described in Claims 1 to 3 utilizes pressure differential or an oil pump.
  • Figure 1 is a sectional view showing the entire composition of an embodiment of the scroll compressor in accordance with the aspect of the invention.
  • Figure 2 is an enlarged schematic representation of portion A of Fig. 1.
  • Figure 3 is a schematic representation illustrative of the position of the oil injection of another scroll compressor in accordance with the invention.
  • the compressor shown in Fig. 1 is a scroll compressor 120 equipped with a cylindrical hermetic housing 121 having its both ends closed. Housed in the hermetic housing 121 are an electric element 122 and a scroll compression element 123 driven by the electric element 122.
  • the electric element 122 has a stator 124 fixed in the hermetic housing 121 and a rotor 125 positioned at the center of the stator 124.
  • a rotating shaft 126 oriented in the direction of the axial center of the hermetic housing 121 is connected to the center of the rotor 125 in a penetrating fashion, and one end thereof penetrates the center of a support frame 127 supporting the scroll compression element 123 so that it is rotatably supported.
  • the support frame 127 is connected and secured to the inner wall surface of the hermetic housing 121.
  • the middle portion near one end of the rotating shaft 126 is rotatably supported by a bearing 128 of the support frame 127, and the rotor 125 is supported on the inner wall surface of the hermetic housing 121 via the rotating shaft 126 and the support frame 127.
  • the central part of one end of the rotating shaft 126 penetrating the support frame 127 is formed as a pin or crank 129 provided eccentrically in relation to the axial center of the rotating shaft 126.
  • a swivel scroll 130 is joined to the pin 129.
  • the swivel scroll 130 is provided with a boss hole 131 in which the pin 129 is inserted for connection to the center of one side surface of a discoid panel board, and a spiral lap 132 formed on the other side surface of the panel board.
  • a stationary scroll 133 is joined to the support frame 127.
  • the stationary scroll 133 has a spiral lap 135 positioned in a zigzag fashion with respect to the lap 132 of the swivel scroll 130 so as to form a plurality of compression chambers 134.
  • an intake pipe 136 for refrigerant gas that penetrates the hermetic housing 121.
  • a discharge port 137 for discharging a compressed refrigerant gas into the hermetic housing 121.
  • the intake side of the scroll compression element 123 of the refrigerant gas introduced through the intake pipe 136, the rear surface of the swivel scroll 130, i.e. the surface of the side where the boss hole 131 of the panel board is located, and the support frame 127 are in communication at the peripheral portion of the panel board of the swivel scroll 130.
  • the pressure among those places is nearly as low as that at the foregoing refrigerant gas intake side and it is lower than the pressure in the hermetic housing 121.
  • a differential lubricating portion 138 is provided on the other end of the rotating shaft 126.
  • the lubricating portion 138 is installed in the hermetic housing 121 to rotatably support the rotating shaft 126 and it is equipped with an auxiliary support frame 141 having an auxiliary bearing 140 with an oil introducing pipe 139 attached thereto.
  • a bearing 142 is installed between the auxiliary support frame 141 and the rotating shaft 126, a receiving portion 143 of the bearing 142 being provided on the auxiliary bearing 140.
  • the rotating shaft 126 has an oil feed passage 144 extending from one end to the other end thereof.
  • a small hole 145 communicating the oil feed passage 144 with the sliding surface of the bearing 128 is provided in the middle of the portion where the rotating shaft 126 is rotatably supported by the bearing 128.
  • a spiral groove 146 in communication with the small hole 145 is provided in the surface of the rotating shaft 126, beginning from the outlet of the small hole 145 and extending toward the electric element 122 until the portion where the rotating shaft 126 is rotatably supported by the bearing 128.
  • the lubricant that has left one end of the rotating shaft 126 gas-seals the boss hole 131 and the sliding surface of the pin 129, and the lubricant that has passed through the small hole 145 flows through the groove 146 to lubricate the sliding surface and also to gas-seal the sliding surface on the side of the scroll compression element 123 from the small hole 145.
  • the hermetic housing 121 is filled with the lubricant "b" up to a predetermined level.
  • the lubricant "b” is sucked up from the lubricating portion 138 by the pressure differential mentioned above and it passes through the oil feed passage 144 provided in the rotating shaft 126 to be fed to respective sliding portions including the bearing 128.
  • the lubricant is circulated for repeated use.
  • an oil injection mechanism 151 for injecting and supplying the lubricant is provided in the vicinity of an intake position 150 where the refrigerant gas is introduced from outside the hermetic housing 121 into the scroll compression element 123 via the intake pipe 136.
  • the oil injection mechanism 151 is fixed to the support frame 127; it is composed of an oil nozzle 153 for injecting a lubricant through an oil feed passage 152 and a valve 156 that opens/closes an oil feed passage inlet 155 of the oil nozzle 153 by utilizing the elasticity of a spring 154.
  • Reference numeral 157 denotes a fixing plug for fixing the oil injection mechanism 151
  • reference numeral 158 denotes a lubricant return passage
  • reference numeral 159 denotes a lubricant branch passage.
  • the oil injection mechanism 151 may be fixed at other location than the support frame 127; it may be secured, for example, to the stationary scroll 133.
  • the valve 156 shown in Fig. and Fig. 2 is shaped like a cap that is capable of housing a part of the spring 154; it may, however, be shaped like a plate. In other words, there is no particular restriction on the shape of the valve.
  • the clearance between the valve 156 and the support frame 127 fixing the valve 156, the diameter and the length of the oil feed passage 152 are to be determined properly.
  • the refrigerant gas is sucked in through the intake pipe 136 to the intake position 150 of the outer peripheral portion of the scroll compression element 123, and compressed as it gradually moves toward the center of the scroll compressor.
  • the refrigerant gas is discharged into the hermetic housing 121 through the discharge port 137 provided at the center of the stationary scroll 133 and the accompanying lubricant is separated in this space, thus suppressing pulsation.
  • the discharged gas flows through passages (not shown) provided in the stationary scroll 133 and the support frame 127 as indicated by the white arrows and reaches the electric element 122 side.
  • the lubricant in the refrigerant gas is further separated primarily by the centrifugal force generated by the rotation of the rotor 125 and by the baffle plate effect due to the stator 124, the auxiliary support frame 141, etc., then the refrigerant gas from which the lubricant has been separated is discharged out of the hermetic housing 121 through a discharge pipe 147.
  • the separated lubricant flows as indicated by the black arrows and accumulates at the bottom of the hermetic housing 121 and it is circulated for repeated use.
  • the refrigerant gas intake side, the rear surface of the swivel scroll 130, and the support frame 127 are in communication; hence, the pressure among those places is substantially as low as that at the refrigerant gas intake side and it is lower than the pressure in the hermetic housing 121.
  • This pressure differential causes the lubricant "b" to be sucked up through the oil introducing pipe 139 of the lubricating portion 138 and supplied under high pressure via the oil feed passage 144 provided in the rotating shaft 126, as indicated by the black arrows.
  • a part of the supplied high-pressure lubricant passes through the small hole 145 as indicated by the black arrows and flows through the groove 146 toward the electric element 122 to lubricate sliding surfaces before it reaches the bottom of the hermetic housing 121.
  • the clearance between the rotating shaft 126 and the bearing 128 is extremely small.
  • the clearance is set, for example, to approximately 10 to 30 m; hence, the sliding portions of the rotating shaft 126 and the bearing 128 on the side of the scroll compression element 123 from the small hole 145 is well gas-sealed.
  • the high-pressure lubricant leaving one end of the rotating shaft 126 gas-seals the boss hole 131 and the sliding surface of the pin 129. After that, these lubricants flow between the swivel scroll 130 and the support frame 127 as indicated by the black arrows to lubricate the groove of an Oldham ring 148, then flows along the outer periphery of the panel board of the swivel scroll 130 to be supplied to the refrigerant gas intake side in the scroll compression element 123 to lubricate sliding surfaces. The lubricant is then discharged together with the compressed gas through the discharge port 137 into the hermetic housing 121, and separated from the compressed gas before reaching the bottom of the hermetic housing 121.
  • the Oldham ring 148 is installed between the support frame 127 and the swivel scroll 130; it is revolved on a circular orbit by being driven by the electric element 122 so that the swivel scroll 130 does not rotate with respect to the stationary scroll 133.
  • this lubricating system is good enough to sufficiently lubricate the sliding surfaces of the scroll compression element 123. If the rotational speed of the rotating shaft 126 is low, then this lubricating system is not good enough; therefore, the oil injection mechanism 151 is actuated to inject and supply the lubricant if the rotational speed of the rotating shaft 126 is low.
  • the pressure in the hermetic housing 121 acts, via the lubricant, on the rear surface on the side of the fixing plug 157 of the valve 156 of the oil injection mechanism 151.
  • the high elasticity of the spring 154 causes the valve 156 to push toward the fixing plug 157 to keep the oil feed passage inlet 155 open. Therefore, the lubricant held in the hermetic housing 121 flows in the direction indicated by the arrows via the lubricant return passage 158 and the lubricant branch passage 159, passes through the intake position 150 before it is injected to the scroll compression element 123.
  • the pressure differential When the pressure differential is high, the pressure differential causes the valve 156 to overcome the elasticity of the spring 154 and moves toward the oil nozzle 153, and the inner surface of the valve 156 comes in contact with the oil feed passage inlet 155 to close it, thus stopping the injection of the lubricant.
  • the amount of injected lubricant is preferably about 3% at the maximum for the elimination volume per unit time.
  • the absence of the oil injection deteriorates the sealing performance; however, if the injection amount exceeds 3 %, then the volume effect deteriorates.
  • the amount of the lubricant to be injected should be determined to obtain the best possible balance of the two factors.
  • the pressure differential for actuating the oil injection mechanism 151 is not particularly restricted. It is preferable, however, to normally set the pressure differential so that the valve 156 opens the oil feed passage inlet 155 to inject the lubricant when the pressure differential is lower than the range from about 4x10 5 to 8x10 5 N/m 2 (4 to about 8 kgf/cm 2 ).
  • Figure 3 shows the position where the lubricant is injected to the scroll compression element of another scroll compressor in accordance with the present invention.
  • the oil injection mechanism 151 (not shown) is provided at a location in the vicinity of a communication passage 161 located between a first suction inlet 160 provided on the stationary scroll 133 for taking the refrigerant gas into the scroll compression element 123 from outside the hermetic housing 121 and a second suction inlet 162 that is provided on the stationary scroll 133 at the position opposed to the first suction inlet 160 and that is in communication with the communication passage 161.
  • the oil injection mechanism 151 is provided at the location in the vicinity of the communication passage 161 between a line "a" connecting a center 163 of the rotating shaft 126 and a center 164 of the first suction inlet 160 and a line “c” drawn 90 degrees away from the center 163 of the rotating shaft 126 toward the second suction inlet 162, using the line “a” as the baseline.
  • the lubricant is injected from the oil injection mechanism 151 to the communication passage 161 located between the line "a” and the line "c" (an example of the injecting position is indicated by the black arrow). Except this part of constitution, this scroll compressor in accordance with the invention shares the same constitution as that of the scroll compressor 120 shown in Fig. 1 and Fig. 2.
  • the refrigerant gas is introduced through the two places, namely, the first suction inlet 160 and the second suction inlet 162, so that the intake efficiency of the refrigerant gas is improved. Moreover, the lubricant that has been injected at the particular position of the communication passage 161 is uniformly supplied to the scroll compression element 123 by the refrigerant gas that has been taken in; therefore, the sealing performance and lubricating performance are further improved.
  • HFC-based refrigerants such as 1, 1, 1,2-tetrafluoroethane (R134a) simple substance, a mixed refrigerant (R407C) of R 134a, difluoromethane (R-32), and pentafluoroethane (R-125), and the mixed refrigerant (R410A) of R-32 and R-125, or HCFC-based refrigerants such as a simple substance or a mixed refrigerant of hydrochloro-difluoromethane (R22).
  • HFC-based refrigerants such as 1, 1, 1,2-tetrafluoroethane (R134a) simple substance, a mixed refrigerant (R407C) of R 134a, difluoromethane (R-32), and pentafluoroethane (R-125), and the mixed refrigerant (R410A) of R-32 and R-125, or HCFC-based refrigerants such as a simple substance or
  • lubricant employed in the present invention are ester-based oils or ether-based oils compatible with the refrigerants mentioned above, or alkylbenzene-based oils incompatible with the refrigerants, or mixtures of these.
  • scroll compressor in accordance with the present invention refers to a horizontal type scroll compressor.
  • the scroll compressor in accordance with the invention is not limited to the horizontal type; the invention is applicable also to a vertical scroll compressor or other types of scroll compressors.
  • the scroll compressor in accordance with the invention is equipped with the oil injection mechanism of the simple construction that makes it easy to avoid insufficient lubricant supplied to the scroll compression element when the number of revolutions of the rotating shaft decreases thereby to permit stable operation with good sealing and lubricating performance, high reliability, and high compression efficiency over an extended period of time.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention
The present invention relates to a scroll compressor mounted on an air conditioner, a refrigerating machine, etc. and, more particularly, to a scroll compressor adapted to discharge compressed gas, which has been compressed in a plurality of compression chambers formed by the engagement between a stationary scroll and a swivel scroll, out of a hermetic housing.
2. Description of Related Art
A scroll compressor employed for a refrigerating cycle of an air conditioner or the like is constructed as shown in Fig 4 as disclosed, for example, in Japanese Examined Patent Publication No. 7-99150.
A cylindrical hermetic housing 101 with its both ends closed includes an electric element 102 and a scroll compression element 103 therein. The electric element 102 is composed of a stator 104 secured to the inner wall surface of the hermetic housing 101 and a rotor 105 rotatably supported in the stator 104, a rotating shaft 106 being connected to the rotor 105 in a penetrating fashion. One end of the rotating shaft 106 is rotatably supported on a support frame 107 partly constituting the scroll compression element 103. The other end of the rotating shaft 106 juts out of the rotor 105, a displacement pump 108 such as a trochoid pump, rotary pump, or reciprocating pump being connected to the distal end thereof. An oil inlet pipe 109 is connected to an end of the displacement pump 108. The end of the intake side of the oil inlet pipe 109 is extended downward so that it is submerged in a lubricant "b" contained in the hermetic housing 101.
An oil feed passage for taking in the lubricant "b" by the displacement pump 108 is bored in the rotating shaft 106 in the axial direction, so that the lubricant is recirculated after it is supplied to sliding parts such as the support frame 107.
The central part of one end of the rotating shaft 106 supported by the support frame 107 in the penetrating manner is formed as a pin or crank 110 provided eccentrically in relation to the axial center of the rotating shaft 106. A swivel scroll 111 is connected to the pin 110. The swivel scroll 111 is formed into a discoid shape, a boss hole 112 for connection with the pin 110 being formed at the center of one side surface thereof, while a spiral lap 113 is integrally formed on the other side surface of the swivel scroll 111.
Joined to the support frame 107 is a stationary scroll 114. The stationary scroll 114 has a spiral lap 115 formed on a portion thereof opposed to the swivel scroll 111, and also a plurality of compression chambers 116 formed between itself and the lap 113. These compression chambers 116 such in a refrigerant gas through the outer peripheral portion thereof and reduces the volumes as they move toward the center so as to compress the refrigerant gas.
A discharge port 117 is formed at the center of the stationary scroll 114. The stationary scroll 114 is provided with a muffler 118 that surrounds the outer side of the discharge port 117.
There has also been proposed a horizontal type scroll compressor under Japanese Examined Patent Publication No. 3-175186. This type does not employ the pump for supplying a lubricant, and it discharges compressed gas into a hermetic housing; it has a through hole in the swivel scroll to communicate an appropriate compression chamber among the scroll compression elements, the rear surface of the swivel scroll, and the support frame so as to set the pressure among them to an appropriate medium pressure, e.g. 8 to 9 kg/cm2 that is lower than the pressure, e.g. 15 to 25 kg/cm2, in a hermetic housing. By utilizing the pressure differential, a lubricant is sucked up and passed through the oil feed passage provided in the rotating shaft to be supplied to respective sliding parts including a support frame. The swivel scroll is pressed against a stationary scroll by the foregoing pressure to bring them into contact so as to provide gas seal thereby to compress the refrigerant gas.
However, regardless of whether the lubrication is conducted using a pump or pressure differential, there has been the problem described below. The amount of a lubricant supplied varies according to the number of revolutions of the rotating shaft; therefore, a sufficient amount of the lubricant is supplied as long as the number of revolutions is sufficiently large, but if the number of revolutions decreases, then the amount of the lubricant supplied decreases. As a result, the an insufficient amount of the lubricant is supplied, for example, to a plurality of the compression chambers 116 formed between the lap 115 and the lap 113, and the lubricating and sealing performance deteriorates with resultant deterioration of the whole performance, meaning deteriorated reliability.
JP 06 058270 A and JP 06 058273A disclose a scroll compressor which is constituted so that oil is not injected into a compressor element at the time of a high circulating quantity of gas fluid, but oil is injected only at the time of a low circulating quantity.
It is an object of the present invention to provide an improved scroll compressor.
SUMMERY OF THE INVENTION
The inventors have enthusiastically studied to solve the problem and found a solution thereto, which has led to the accomplishment of the present invention. According to the solution, a separate oil injection mechanism having a particular composition is installed in a particular position in the scroll compression element. Accordingly, it is an object of the present invention to provide a highly reliable scroll compressor with an improved oil injection mechanism. To solve the problem, there is provided a highly reliable scroll compressor equipped with an oil injection mechanism having a simple constitution in accordance with one aspect of the present invention. This scroll compressor makes it possible to easily avoid insufficient supply of the lubricant to the compression chambers even when the number of revolutions of the rotary shaft decreases.
A scroll compressor according to Claim 1 of the present invention is equipped with an electric element and a scroll compression element driven by a rotating shaft of the electric element that are placed in a hermetic housing, a lubricant contained in the hermetic housing, and a lubricating portion provided on an end of the rotating shaft to supply the lubricant from the lubricating portion to respective sliding portions via an oil feed passage provided in the rotating shaft and to circulate it for reuse, wherein: an oil injection mechanism composed of an oil nozzle for injecting oil and a valve for opening/closing an oil feed passage inlet of the oil nozzle by the elasticity of a spring is provided in the vicinity of the position where a refrigerant gas is sucked into the scroll compression element from outside the hermetic housing, so that the valve opens the oil feed passage inlet to inject the lubricant held in the hermetic housing into the scroll compression element if the difference between the pressure in the hermetic housing that acts on the rear surface of the valve and the pressure in the vicinity of the position, where the refrigerant gas is taken in, that acts on the outlet of the oil nozzle is small, whereas the valve closes the oil feed passage inlet to stop the injection of the lubricant if the pressure differential is large.
According to another aspect of the invention described in Claim 2 of the present invention, the injection amount of the lubricant is 0.1 to 3% for the elimination volume per unit time in the scroll compressor described in Claim 1.
According to yet another aspect of the invention described in Claim 3 of the present invention, the valve opens the oil feed passage inlet to inject the lubricant if the pressure differential is less than the range of 4x105 to 8x105 N/m2(4 to 8 kgf/cm2) in the scroll compressor described in Claims 1 or 2.
According to a further aspect of the invention described in Claim 4 of the invention, the lubrication system in the lubricating portion in the scroll compressor described in Claims 1 to 3 utilizes pressure differential or an oil pump.
BRIEF DESCRIPTION OF THE DRAWINGS
  • Fig. 1 is a sectional view showing the entire composition of an embodiment of the scroll compressor in accordance with an aspect of the present invention.
  • Fig. 2 is an enlarged schematic representation of portion A of Fig. 1.
  • Fig. 3 is a schematic representation showing the position where a lubricant is injected to a scroll compression element of another scroll compressor in accordance with the present invention.
  • Fig. 4 is a sectional view showing the entire composition of a conventional scroll compressor.
    • DESCRIPTION OF THE PREFERRED EMBODIMENTS
    An aspect of the present invention related to Claims 1 to 4 of the present application will now be described in conjunction with Fig. 1 through Fig. 4.
    Figure 1 is a sectional view showing the entire composition of an embodiment of the scroll compressor in accordance with the aspect of the invention. Figure 2 is an enlarged schematic representation of portion A of Fig. 1. Figure 3 is a schematic representation illustrative of the position of the oil injection of another scroll compressor in accordance with the invention.
    The compressor shown in Fig. 1 is a scroll compressor 120 equipped with a cylindrical hermetic housing 121 having its both ends closed. Housed in the hermetic housing 121 are an electric element 122 and a scroll compression element 123 driven by the electric element 122.
    The electric element 122 has a stator 124 fixed in the hermetic housing 121 and a rotor 125 positioned at the center of the stator 124. A rotating shaft 126 oriented in the direction of the axial center of the hermetic housing 121 is connected to the center of the rotor 125 in a penetrating fashion, and one end thereof penetrates the center of a support frame 127 supporting the scroll compression element 123 so that it is rotatably supported. In this case, the support frame 127 is connected and secured to the inner wall surface of the hermetic housing 121. The middle portion near one end of the rotating shaft 126 is rotatably supported by a bearing 128 of the support frame 127, and the rotor 125 is supported on the inner wall surface of the hermetic housing 121 via the rotating shaft 126 and the support frame 127.
    The central part of one end of the rotating shaft 126 penetrating the support frame 127 is formed as a pin or crank 129 provided eccentrically in relation to the axial center of the rotating shaft 126. A swivel scroll 130 is joined to the pin 129. The swivel scroll 130 is provided with a boss hole 131 in which the pin 129 is inserted for connection to the center of one side surface of a discoid panel board, and a spiral lap 132 formed on the other side surface of the panel board.
    A stationary scroll 133 is joined to the support frame 127. The stationary scroll 133 has a spiral lap 135 positioned in a zigzag fashion with respect to the lap 132 of the swivel scroll 130 so as to form a plurality of compression chambers 134.
    Connected to the side wall surface of the stationary scroll 133 is an intake pipe 136 for refrigerant gas that penetrates the hermetic housing 121. Provided at the center of the stationary scroll 133 is a discharge port 137 for discharging a compressed refrigerant gas into the hermetic housing 121.
    The intake side of the scroll compression element 123 of the refrigerant gas introduced through the intake pipe 136, the rear surface of the swivel scroll 130, i.e. the surface of the side where the boss hole 131 of the panel board is located, and the support frame 127 are in communication at the peripheral portion of the panel board of the swivel scroll 130. Hence, the pressure among those places is nearly as low as that at the foregoing refrigerant gas intake side and it is lower than the pressure in the hermetic housing 121.
    A differential lubricating portion 138 is provided on the other end of the rotating shaft 126. The lubricating portion 138 is installed in the hermetic housing 121 to rotatably support the rotating shaft 126 and it is equipped with an auxiliary support frame 141 having an auxiliary bearing 140 with an oil introducing pipe 139 attached thereto. A bearing 142 is installed between the auxiliary support frame 141 and the rotating shaft 126, a receiving portion 143 of the bearing 142 being provided on the auxiliary bearing 140.
    The rotating shaft 126 has an oil feed passage 144 extending from one end to the other end thereof. A small hole 145 communicating the oil feed passage 144 with the sliding surface of the bearing 128 is provided in the middle of the portion where the rotating shaft 126 is rotatably supported by the bearing 128. A spiral groove 146 in communication with the small hole 145 is provided in the surface of the rotating shaft 126, beginning from the outlet of the small hole 145 and extending toward the electric element 122 until the portion where the rotating shaft 126 is rotatably supported by the bearing 128. The lubricant that has left one end of the rotating shaft 126 gas-seals the boss hole 131 and the sliding surface of the pin 129, and the lubricant that has passed through the small hole 145 flows through the groove 146 to lubricate the sliding surface and also to gas-seal the sliding surface on the side of the scroll compression element 123 from the small hole 145.
    The hermetic housing 121 is filled with the lubricant "b" up to a predetermined level. The lubricant "b" is sucked up from the lubricating portion 138 by the pressure differential mentioned above and it passes through the oil feed passage 144 provided in the rotating shaft 126 to be fed to respective sliding portions including the bearing 128. The lubricant is circulated for repeated use.
    According to the invention, an oil injection mechanism 151 for injecting and supplying the lubricant is provided in the vicinity of an intake position 150 where the refrigerant gas is introduced from outside the hermetic housing 121 into the scroll compression element 123 via the intake pipe 136.
    As shown in Fig. 2, the oil injection mechanism 151 is fixed to the support frame 127; it is composed of an oil nozzle 153 for injecting a lubricant through an oil feed passage 152 and a valve 156 that opens/closes an oil feed passage inlet 155 of the oil nozzle 153 by utilizing the elasticity of a spring 154. Reference numeral 157 denotes a fixing plug for fixing the oil injection mechanism 151, reference numeral 158 denotes a lubricant return passage, and reference numeral 159 denotes a lubricant branch passage. The oil injection mechanism 151 may be fixed at other location than the support frame 127; it may be secured, for example, to the stationary scroll 133.
    The valve 156 shown in Fig. and Fig. 2 is shaped like a cap that is capable of housing a part of the spring 154; it may, however, be shaped like a plate. In other words, there is no particular restriction on the shape of the valve. The clearance between the valve 156 and the support frame 127 fixing the valve 156, the diameter and the length of the oil feed passage 152 are to be determined properly.
    When the operation of the horizontal type scroll compressor 120 having the constitution described above is begun, the refrigerant gas is sucked in through the intake pipe 136 to the intake position 150 of the outer peripheral portion of the scroll compression element 123, and compressed as it gradually moves toward the center of the scroll compressor. The refrigerant gas is discharged into the hermetic housing 121 through the discharge port 137 provided at the center of the stationary scroll 133 and the accompanying lubricant is separated in this space, thus suppressing pulsation.
    The discharged gas flows through passages (not shown) provided in the stationary scroll 133 and the support frame 127 as indicated by the white arrows and reaches the electric element 122 side. And the lubricant in the refrigerant gas is further separated primarily by the centrifugal force generated by the rotation of the rotor 125 and by the baffle plate effect due to the stator 124, the auxiliary support frame 141, etc., then the refrigerant gas from which the lubricant has been separated is discharged out of the hermetic housing 121 through a discharge pipe 147. The separated lubricant flows as indicated by the black arrows and accumulates at the bottom of the hermetic housing 121 and it is circulated for repeated use.
    Although it is not illustrated, the refrigerant gas intake side, the rear surface of the swivel scroll 130, and the support frame 127 are in communication; hence, the pressure among those places is substantially as low as that at the refrigerant gas intake side and it is lower than the pressure in the hermetic housing 121. This pressure differential causes the lubricant "b" to be sucked up through the oil introducing pipe 139 of the lubricating portion 138 and supplied under high pressure via the oil feed passage 144 provided in the rotating shaft 126, as indicated by the black arrows. A part of the supplied high-pressure lubricant passes through the small hole 145 as indicated by the black arrows and flows through the groove 146 toward the electric element 122 to lubricate sliding surfaces before it reaches the bottom of the hermetic housing 121. The clearance between the rotating shaft 126 and the bearing 128 is extremely small. The clearance is set, for example, to approximately 10 to 30 m; hence, the sliding portions of the rotating shaft 126 and the bearing 128 on the side of the scroll compression element 123 from the small hole 145 is well gas-sealed.
    The high-pressure lubricant leaving one end of the rotating shaft 126 gas-seals the boss hole 131 and the sliding surface of the pin 129. After that, these lubricants flow between the swivel scroll 130 and the support frame 127 as indicated by the black arrows to lubricate the groove of an Oldham ring 148, then flows along the outer periphery of the panel board of the swivel scroll 130 to be supplied to the refrigerant gas intake side in the scroll compression element 123 to lubricate sliding surfaces. The lubricant is then discharged together with the compressed gas through the discharge port 137 into the hermetic housing 121, and separated from the compressed gas before reaching the bottom of the hermetic housing 121.
    The Oldham ring 148 is installed between the support frame 127 and the swivel scroll 130; it is revolved on a circular orbit by being driven by the electric element 122 so that the swivel scroll 130 does not rotate with respect to the stationary scroll 133.
    As long as the rotational speed of the rotating shaft 126 is high, this lubricating system is good enough to sufficiently lubricate the sliding surfaces of the scroll compression element 123. If the rotational speed of the rotating shaft 126 is low, then this lubricating system is not good enough; therefore, the oil injection mechanism 151 is actuated to inject and supply the lubricant if the rotational speed of the rotating shaft 126 is low.
    The pressure in the hermetic housing 121 acts, via the lubricant, on the rear surface on the side of the fixing plug 157 of the valve 156 of the oil injection mechanism 151. When the difference between the pressure in the hermetic housing 121 and the pressure in the vicinity of the refrigerant gas intake position 150 acting on the outlet side of the oil nozzle 153 is small, the high elasticity of the spring 154 causes the valve 156 to push toward the fixing plug 157 to keep the oil feed passage inlet 155 open. Therefore, the lubricant held in the hermetic housing 121 flows in the direction indicated by the arrows via the lubricant return passage 158 and the lubricant branch passage 159, passes through the intake position 150 before it is injected to the scroll compression element 123.
    When the pressure differential is high, the pressure differential causes the valve 156 to overcome the elasticity of the spring 154 and moves toward the oil nozzle 153, and the inner surface of the valve 156 comes in contact with the oil feed passage inlet 155 to close it, thus stopping the injection of the lubricant.
    As set forth above, it is important to adjust the elasticity of the spring 154 so that, if the rotational speed of the rotating shaft 126 is high and the pressure in the hermetic housing 121 becomes higher than a predetermined level, then the injection of the lubricant by the oil injection mechanism is stopped, and if the rotational speed of the rotating shaft 126 is low and the pressure in the hermetic housing 121 becomes lower than the predetermined level, then the lubricant is injected by the oil injection mechanism 151.
    The amount of injected lubricant is preferably about 3% at the maximum for the elimination volume per unit time. The absence of the oil injection deteriorates the sealing performance; however, if the injection amount exceeds 3 %, then the volume effect deteriorates. Hence, the amount of the lubricant to be injected should be determined to obtain the best possible balance of the two factors.
    The pressure differential for actuating the oil injection mechanism 151 is not particularly restricted. It is preferable, however, to normally set the pressure differential so that the valve 156 opens the oil feed passage inlet 155 to inject the lubricant when the pressure differential is lower than the range from about 4x105 to 8x105 N/m2 (4 to about 8 kgf/cm2).
    Figure 3 shows the position where the lubricant is injected to the scroll compression element of another scroll compressor in accordance with the present invention. The oil injection mechanism 151 (not shown) is provided at a location in the vicinity of a communication passage 161 located between a first suction inlet 160 provided on the stationary scroll 133 for taking the refrigerant gas into the scroll compression element 123 from outside the hermetic housing 121 and a second suction inlet 162 that is provided on the stationary scroll 133 at the position opposed to the first suction inlet 160 and that is in communication with the communication passage 161. In addition, the oil injection mechanism 151 is provided at the location in the vicinity of the communication passage 161 between a line "a" connecting a center 163 of the rotating shaft 126 and a center 164 of the first suction inlet 160 and a line "c" drawn 90 degrees away from the center 163 of the rotating shaft 126 toward the second suction inlet 162, using the line "a" as the baseline. The lubricant is injected from the oil injection mechanism 151 to the communication passage 161 located between the line "a" and the line "c" (an example of the injecting position is indicated by the black arrow). Except this part of constitution, this scroll compressor in accordance with the invention shares the same constitution as that of the scroll compressor 120 shown in Fig. 1 and Fig. 2.
    The refrigerant gas is introduced through the two places, namely, the first suction inlet 160 and the second suction inlet 162, so that the intake efficiency of the refrigerant gas is improved. Moreover, the lubricant that has been injected at the particular position of the communication passage 161 is uniformly supplied to the scroll compression element 123 by the refrigerant gas that has been taken in; therefore, the sealing performance and lubricating performance are further improved.
    Specific examples of the refrigerant employed in the present invention are HFC-based refrigerants such as 1, 1, 1,2-tetrafluoroethane (R134a) simple substance, a mixed refrigerant (R407C) of R 134a, difluoromethane (R-32), and pentafluoroethane (R-125), and the mixed refrigerant (R410A) of R-32 and R-125, or HCFC-based refrigerants such as a simple substance or a mixed refrigerant of hydrochloro-difluoromethane (R22).
    Specific examples of the lubricant employed in the present invention are ester-based oils or ether-based oils compatible with the refrigerants mentioned above, or alkylbenzene-based oils incompatible with the refrigerants, or mixtures of these.
    The above description of the scroll compressor in accordance with the present invention refers to a horizontal type scroll compressor. The scroll compressor in accordance with the invention, however, is not limited to the horizontal type; the invention is applicable also to a vertical scroll compressor or other types of scroll compressors.
    The scroll compressor in accordance with the invention is equipped with the oil injection mechanism of the simple construction that makes it easy to avoid insufficient lubricant supplied to the scroll compression element when the number of revolutions of the rotating shaft decreases thereby to permit stable operation with good sealing and lubricating performance, high reliability, and high compression efficiency over an extended period of time.

    Claims (4)

    1. A scroll compressor (120) comprising: an electric element (122) and a scroll compression element (123) driven by a rotating shaft (126) of said electric element (122) that are housed in a hermetic housing (121), a lubricant (b) contained in said hermetic housing (121), and a lubricating portion (138) provided on an end of said rotating shaft (126), the lubricant (b) being supplied from said lubricating portion (138) to respective sliding portions via an oil feed passage (144) provided in said rotating shaft (126) and circulate it for reuse, wherein: an oil injection mechanism (151) composed of an oil nozzle (153) for injecting oil and a valve (156) for opening/closing an oil feed passage inlet (155) of said oil nozzle (153) is provided, characterized in that the oil injection mechanism (151) is provided in the vicinity of a position where a refrigerant gas is sucked into said scroll compression element (123) from outside said hermetic housing (121) so that said valve (156), which utilizes the elasticity of a spring (154) opens said oil feed passage inlet (155) to inject the lubricant (b) held in said hermetic housing (121) into said scroll compression element (123) if the difference between the pressure in said hermetic housing (121) that acts on the rear surface of said valve (156) and the pressure in the vicinity of said position, where the refrigerant gas is sucked in, that acts on an outlet of said oil nozzle (153) is small, whereas said valve (156) closes said oil feed passage inlet (155) to stop the injection of the lubricant (b) if said pressure differential is large.
    2. A scroll compressor (120) according to claim 1, wherein the injection amount of the lubricant (b) is set to 0.1 to 3% for the elimination volume per unit time.
    3. A scroll compressor (120) according to claim 1 or 2, wherein said valve (156) opens said oil feed passage inlet (155) to inject the lubricant (b) if said pressure differential is less than a range of 4·105 to 8·105 N/m2 (4 to 8 kgf/cm2).
    4. A scroll compressor (120) according to claim 1 to 3, wherein a lubrication system in said lubricating portion utilizes pressure differential or an oil pump.
    EP03006364A 1997-09-26 1998-09-16 Scroll compressor Expired - Lifetime EP1319838B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    JP26193397A JP3448469B2 (en) 1997-09-26 1997-09-26 Scroll compressor
    JP26193397 1997-09-26
    EP98117556A EP0903499B1 (en) 1997-09-17 1998-09-16 Scroll compressor

    Related Parent Applications (2)

    Application Number Title Priority Date Filing Date
    EP98117556.5 Division 1998-09-16
    EP98117556A Division EP0903499B1 (en) 1997-09-17 1998-09-16 Scroll compressor

    Publications (2)

    Publication Number Publication Date
    EP1319838A1 EP1319838A1 (en) 2003-06-18
    EP1319838B1 true EP1319838B1 (en) 2005-07-27

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    EP03006364A Expired - Lifetime EP1319838B1 (en) 1997-09-26 1998-09-16 Scroll compressor
    EP03006365A Expired - Lifetime EP1319839B1 (en) 1997-09-26 1998-09-16 Scroll compressor

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    EP03006365A Expired - Lifetime EP1319839B1 (en) 1997-09-26 1998-09-16 Scroll compressor

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    JP (1) JP3448469B2 (en)
    DE (2) DE69831023T2 (en)
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    JP4321220B2 (en) * 2003-11-05 2009-08-26 三菱電機株式会社 Scroll compressor
    JP4845409B2 (en) * 2005-03-31 2011-12-28 三洋電機株式会社 Hermetic compressor
    CN101484704B (en) * 2007-01-30 2013-05-22 三菱重工业株式会社 Cyclone compressor
    JP6927164B2 (en) 2018-06-29 2021-08-25 株式会社デンソー Horizontal scroll compressor
    CN110360103B (en) * 2019-07-17 2020-12-25 珠海格力节能环保制冷技术研究中心有限公司 Scroll compressor, air conditioner and vehicle
    CN113931844B (en) * 2021-11-23 2023-09-22 珠海凌达压缩机有限公司 Compressor gleitbretter subassembly reaches compressor including it

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    JPS58172404A (en) * 1982-04-05 1983-10-11 Hitachi Ltd Scroll fluid machine
    JPS59141785A (en) * 1984-01-26 1984-08-14 Mitsubishi Electric Corp Scroll compressor
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    Also Published As

    Publication number Publication date
    JPH11101187A (en) 1999-04-13
    DE69831023D1 (en) 2005-09-01
    EP1319839A1 (en) 2003-06-18
    EP1319839B1 (en) 2005-07-27
    DE69831023T2 (en) 2006-06-01
    DE69831024D1 (en) 2005-09-01
    ES2246025T3 (en) 2006-02-01
    EP1319838A1 (en) 2003-06-18
    DE69831024T2 (en) 2006-06-01
    JP3448469B2 (en) 2003-09-22
    ES2246024T3 (en) 2006-02-01

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