JP2008169694A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve efficiency in a lubrication pump, without largely increasing processing cost, while securing reduction in a filling quantity of a working fluid, in a scroll compressor. <P>SOLUTION: The scroll compressor has a compressor part, a crankshaft 6, a bearing, the internal gear type lubrication pump 30 having an inner rotor 30a and an outer rotor 30b and feeding oil to the bearing, and a casing for storing these members. The lubrication pump 30 is arranged so as to supply oil of an oil storage part to a back pressure chamber via an oil feeding hole 6 of the crankshaft 6 and the bearing by boosting the oil, and to energize a cover 30a1 covering side surfaces of the inner rotor 30a and the outer rotor 30b to at least any one of the side surface of the inner rotor 30a or the side surface of the outer rotor 30b by thrust force of the crankshaft 6. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a scroll compressor, and particularly suitable for a scroll compressor provided with an oil supply pump that boosts oil and supplies it to a back pressure chamber of a orbiting scroll in a low pressure chamber system in which the pressure in the casing becomes suction pressure. It is.

  The low-pressure chamber type scroll compressor in which the pressure in the casing becomes the suction pressure has the advantage that the amount of working fluid dissolved in the oil stored in the oil storage part is smaller than that of the high-pressure chamber type. ing. In particular, in a scroll compressor used in a refrigeration cycle that encloses a working fluid, when the working fluid is a flammable fluid (for example, hydrocarbon such as propane or butane) or a toxic fluid (for example, ammonia), the working fluid is enclosed. Since a reduction in volume is particularly desirable from a safety standpoint, a low pressure chamber system is particularly desirable.

  However, in the low pressure chamber system, it is necessary to use an oil supply pump with increased pressure in order to supply oil at the suction pressure to the bearing that supports the crankshaft and to flow it to the back chamber of the orbiting scroll.

  As a conventional scroll compressor using an oil pump with pressure increase, there is one disclosed in Japanese Patent Application Laid-Open No. 2001-221175 (Patent Document 1).

  This scroll compressor has a compressor section that compresses a working fluid, a crankshaft that drives the compressor section, a bearing that supports the crankshaft, an inner rotor and an outer rotor, and supplies oil to the bearing. The internal gear type oil supply pump (bearing oil supply part) and a casing (case) that houses the compressor part, the crankshaft, and the oil supply pump are configured.

  And the said casing is providing the oil storage part which stores oil in the said internal space while making internal space into a suction pressure. The compressor part is formed by meshing both scrolls with a fixed scroll having an end plate and a spiral body standing on the end plate, a revolving scroll having an end plate and a spiral body standing on the end plate, and the volume is reduced. A compression chamber that compresses the working fluid, and a back pressure chamber that is provided on the back surface of the orbiting scroll and serves as an intermediate pressure space that is higher than the suction pressure and lower than the discharge pressure. The crankshaft is rotationally driven by a rotational drive source to rotationally drive the orbiting scroll and includes an oil supply hole that serves as an oil supply passage to the bearing.

  The oil supply pump is provided at the end of the crankshaft on the side opposite to the orbiting scroll so as to boost the oil in the oil storage part and supply it to the back pressure chamber through the oil supply hole of the crankshaft and the bearing. The oil pump includes an oil cylinder provided so as to surround a lower end portion of the crankshaft, a pump cover provided on a lower surface of the oil cylinder, an inner rotor and an outer which are housed in a space surrounded by the cylinder and pressurize oil. It consists of a rotor. The oil supply cylinder is fixed to the casing via a support plate, and a shaft thrust surface which is an axial support portion of the crankshaft is arranged at the center of the oil supply cylinder.

JP 2001-221175 A

  In a scroll compressor using an oil pump with pressure increase, the amount of work of the oil pump is larger than when an oil pump without pressure increase is used, and the efficiency of the oil pump is equivalent to the efficiency of the scroll compressor on which it is mounted. It has a great influence. For this reason, it is extremely important to improve the performance of the oil supply pump.

  However, the oil supply pump of Patent Document 1 has a problem that a large amount of oil leaks from the discharge side to the suction side through the side clearance of the inner rotor or the outer rotor, resulting in a reduction in efficiency. As a measure to improve the performance of the oil pump with pressure increase, it is possible to increase the accuracy of each part and reduce the side clearance of the inner rotor or outer rotor to suppress the increase in leakage due to pressure increase. There was a problem of inviting. Note that when the working fluid is a very high pressure fluid such as carbon dioxide, the required back pressure is extremely high. As a result, the amount of pressure required for the oil pump becomes very large, causing internal leakage. There was a problem of inviting an increase.

  An object of the present invention is to realize a scroll compressor with high energy efficiency by realizing an improvement in the efficiency of an oil pump accompanied with pressure increase without significantly increasing the processing cost while ensuring a reduction in the amount of working fluid enclosed by a low-pressure chamber system. Is to provide.

  In order to achieve the above-described object, the present invention includes a compressor section that compresses a working fluid, a crankshaft that drives the compressor section, a bearing that supports the crankshaft, an inner rotor, and an outer rotor. An oil supply pump that supplies oil to the bearing, and a casing that houses the compressor portion, the crankshaft, and the oil supply pump. The casing uses the internal space as a suction pressure, and the internal space. An oil storage section for storing oil, and the compressor section includes a fixed scroll having an end plate and a spiral body standing on the end plate, an orbiting scroll having an end plate and a spiral body standing on the end plate, and the both scrolls. A compression chamber that is formed by meshing and compresses the working fluid by reducing the volume, and is provided at the back of the orbiting scroll and discharges higher than the suction pressure. A back pressure chamber serving as an intermediate pressure space lower than the pressure, and the crankshaft is rotationally driven by a rotational drive source to rotationally drive the orbiting scroll and includes an oil supply hole serving as an oil supply passage to the bearing, In the scroll compressor provided at the end of the crankshaft on the side opposite to the orbiting scroll so as to pressurize the oil in the oil storage section and supply the oil to the back pressure chamber through the oil supply hole of the crankshaft and the bearing. The oil pump urges a cover that covers the side surfaces of the inner rotor and the outer rotor to at least one of the side surface of the inner rotor or the side surface of the outer rotor by a thrust force of the crankshaft. It is in that it was provided.

A more preferable specific configuration example of the present invention is as follows.
(1) The oil pump includes the inner rotor, the outer rotor, a pump cylinder disposed around the outer rotor, and a base plate that covers a side surface of the inner rotor and the outer rotor on the side of the anti-compressor part. The inner rotor and the outer rotor are constituted by an internal gear pump including the cover that covers the side surface of the compressor portion side.
(2) In said (1), the said cover is integrally provided by the same member as the tooth profile part of the said inner rotor, or the tooth profile part of the said outer rotor.
(3) In the above (1), the crankshaft has an oil pump shaft portion having a small diameter at the end on the anti-compressor portion side through a stepped portion, and the inner rotor is the oil pump shaft portion. The cover is sandwiched between a step portion of the crankshaft and at least one of the side surface of the inner rotor and the side surface of the outer rotor.
(4) In the above (1), the crankshaft has an oil pump shaft portion having a small diameter at the end on the side opposite to the compressor portion via a step portion, and the inner rotor is the oil pump shaft portion. The cover is formed of a separate member from the inner rotor and the outer rotor, and at least one of the stepped portion of the crankshaft and the side surface of the inner rotor or the side surface of the outer rotor. Being sandwiched between one side.
(5) In (1), along the crankshaft, the compressor section, the motor serving as the rotational drive source, and the oil pump are mounted in this order on the crankshaft, and the bearing is a compressor of the motor. A main bearing disposed on the part side and a sub-bearing disposed on the anti-compressor part side of the motor, wherein the sub-bearing and the oil pump are disposed adjacent to each other, and the sub-bearing holds the bearing bush and the bearing bush A bearing holder, and the bearing holder and the pump casing are fixedly arranged or integrally formed to form a housing.
(6) In the above (5), the housing communicates between the oil pump and the bearing holder and the oil pump back space formed on the inner surface of the housing and the oil storage space. It is equipped with.
(7) In (6), the communication path is provided with an opening on the oil storage space side lower than the opening on the oil pump back space side.
(8) In the above (5), the crankshaft introduces back pressure that communicates between the oil supply pump back space formed between the oil supply pump and the bearing holder and on the inner surface of the housing, and the oil supply hole. Having a road.
(9) A conforming film is formed on at least one surface that receives the thrust force of the cover, the inner rotor, and the outer rotor.
(10) Back pressure control means for increasing the pressure in the back pressure chamber by a substantially constant value from the suction pressure is provided.

  According to the present invention having such a configuration, it is possible to improve the efficiency of the oil supply pump accompanied by pressure increase without significantly increasing the processing cost while ensuring the reduction of the amount of the working fluid sealed by the low pressure chamber method, and to achieve high energy efficiency. A scroll compressor is provided.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent. In addition, this invention includes making it more effective by combining each embodiment suitably as needed.
(First embodiment)
A scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS.

  First, the overall configuration, function, and operation of the scroll compressor according to the present embodiment will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention.

  The scroll compressor 1 includes a compressor unit 10 that compresses a working fluid, a crankshaft 6 that drives the compressor unit 10, bearings 23, 24, and 25 that support the crankshaft 6, A motor 7 that serves as a rotational drive source, an internal gear type oil pump 30 that supplies oil to the bearings 23, 24, and 25, and a casing 8 that houses the compressor unit 10, the crankshaft 6, the motor 7, and the oil pump 30. And as a main component. The scroll compressor 1 is a vertical scroll compressor in which a crankshaft 6 is arranged vertically and a compressor unit 10, a motor 7 and an oil supply pump 30 are arranged in this order from the top.

  The casing 8 is provided with an oil storage part 125 that stores the oil in the internal space while making the internal space into the suction pressure. The casing 8 includes an upper casing 8b, a cylinder casing 8a, and a bottom casing 8c.

  The compressor unit 10 includes a fixed scroll 2 having a fixed end plate 2b and a fixed spiral body 2a erected on the fixed end plate 2b, a turning scroll 3 having a revolving end plate 3b and a swirl spiral body 3a erected thereon, 3 and a compression chamber 100 that compresses the working fluid by reducing the volume, and a back pressure chamber 110 that is provided on the back surface of the orbiting scroll 3 and serves as an intermediate pressure space that is higher than the suction pressure and lower than the discharge pressure. I have.

  The fixed scroll 2 is mainly composed of a fixed spiral body 2a, a fixed end plate 2b, and an attachment portion 2c around which the attachment surface 2c has a surface substantially the same as the tooth tip of the fixed spiral body 2a. The fixed end plate 2b is provided with a bypass valve 22 composed of a compression spring, a valve plate and a spring retainer for avoiding over-compression and liquid compression, and a discharge port 2d near the center. Further, a suction port 2e for sucking the working fluid is provided on the side surface of the attachment portion 2c.

  The orbiting scroll 3 includes an orbiting spiral body 3a and an orbiting end plate 3b, and an orbiting bearing 23 is provided at the center of the back surface of the orbiting end plate 3b. A main bearing 24 is provided at the center of the frame 4, and the crankshaft 6 is inserted into the main bearing 24. Then, the eccentric pin portion 6 a at the top of the crankshaft 6 is inserted into the orbiting bearing 23, and the orbiting scroll 3 is attached to the frame 4. Here, the Oldham ring 5 is engaged with the frame 4 in order to prevent the orbiting scroll 3 from rotating.

  Next, the fixed scroll 2 is placed from above the orbiting scroll 3 so that the orbiting spiral body 3 a and the fixed spiral body 2 a are engaged with each other, and the attachment portion 2 c of the fixed scroll 2 is screwed to the frame 4. As a result, a plurality of compression chambers 100, which are generally closed spaces between the spiral bodies 3a, 2a, and a suction chamber 105 communicating with the suction port 2c are formed, and a back pressure chamber 110 is formed on the back of the orbiting scroll 3. Is done. Further, a slewing bearing chamber 115 is formed on the upper surface of the pin portion 6a. The rotor 7a is fixed to the crankshaft 6 that projects downward from the frame 4.

  The sub-assembly rotor 7a formed as described above is inserted into the stator 7b fixedly disposed on the cylinder casing 8a, and the fixed scroll 2 of the sub-assembly is fixed to the cylinder casing 8a. Thereby, the motor 7 is formed.

  A sub-bearing support plate 50 is fixed to the lower portion of the cylinder casing 8a, and the lower end portion of the crankshaft 6 projects below the sub-bearing support plate 50 by incorporating the sub-assembly. A sub bearing 25 comprising a ball bush 25a and a ball holder 25b for holding the ball bush 25a is mounted on the protruding lower end of the crankshaft 6, and the ball holder 25b is fixed to the sub bearing support plate 50. An oil supply pump 30 is formed integrally with the sub bearing 25 below the sub bearing 25. Further, the suction pipe 53 is fixed at a position facing the suction port 2e on the side surface of the cylinder casing 8a.

  Next, a fixed cover 51 having a discharge pipe 52 protruding toward the center is screwed to the top of the fixed scroll 2 to form a discharge chamber 120. And after connecting the electric wire from the motor 7 to the internal terminal of the hermetic terminal 54 welded to the upper casing 8b, the upper casing 8b is welded to the cylinder casing 8a. Further, the discharge pipe 52 is brazed to the upper casing 8b. A bottom casing 8c is welded to the bottom of the cylinder casing 8a and the casing 8 is formed by the upper casing 8b, the cylinder casing 8a, and the bottom casing 8c. Thereby, the lower part of casing 8 serves as oil storage part 125 which accumulates oil.

  Next, a specific configuration and operation of the scroll compressor 1 will be described with reference to FIGS. 1 to 4 mainly from the flow of the working fluid and the flow of oil. 2A is a detailed enlarged view of a portion M in FIG. 1, FIG. 2B is an enlarged view of a main portion of FIG. 2A, FIG. 3 is a detailed enlarged view of a portion N of FIG. .

  First, the flow of the working fluid will be mainly described. The working fluid that enters the casing 8 from the suction pipe 53 and uses the suction pressure inside the casing 8 enters the suction chamber 105 through the suction port 2e. Accordingly, the rotation of the crankshaft 6 using the motor 7 as a drive source causes the orbiting scroll 3 to orbit and form a compression chamber 100 between the spiral bodies 2a and 3a. As a result, the working fluid in the suction chamber 105 is confined in the compression chamber 100 and then transferred to the center side while the volume is reduced. In this way, the working fluid whose pressure has been increased to the discharge pressure is discharged from the discharge port 2d or the bypass valve 22 to the discharge chamber 120 and flows out through the discharge pipe 52 to the outside.

  Next, the oil flow will be mainly described. The oil accumulated in the oil storage part 125 is pumped from the lower part to the upper part by the oil supply pump 30 driven by the rotation of the crankshaft 6 through the oil supply vertical hole 6b which is an oil supply hole penetrating the crankshaft 6 in the axial direction. The

  The pumped oil is divided into the four paths described below.

  The first oil supply passage is a sub-bearing oil supply passage for supplying oil to the sub-bearing 25 via the auxiliary bearing oil supply lateral hole 6g. The second oil supply passage is a main bearing oil supply passage with extremely low flow resistance that flows from the main bearing oil supply lateral hole 6c through the main bearing groove 6d to the main bearing 24 and then flows into the back pressure chamber 100. The third oil supply passage is a swing bearing oil supply passage having an extremely small flow resistance, which flows from the swing bearing chamber 115 through the swing bearing groove 6e to the swing bearing 23 and then flows into the back pressure chamber 100. These second and third oil supply passages can be regarded as back pressure chamber inflow passages.

  The fourth oil supply passage is a suction chamber oil supply passage 130 having a throttling action that flows from the swivel bearing chamber 115 through the end plate horizontal hole 3c in the swivel end plate 3b and flows into the suction chamber 105 through the suction chamber pore 3d with restriction. is there. Here, in order to perform the hole processing from the side surface of the swivel end plate 3b, the side plate opening is sealed with a stopper plug.

  The oil that has flowed into the suction chamber 105 through the suction chamber oil supply passage 130 enters the compression chamber 100 together with the working fluid, improves the sealing performance of the compression chamber 100, realizes leakage suppression, and improves the compression performance. Further, since this oil does not pass through the bearing, it is at a low temperature, does not heat the fluid in the suction chamber 105, avoids a decrease in volumetric efficiency, and has an effect of improving the compression performance. As will be described later, since the pressure is reduced in the suction chamber pores 3d, the oil flows into the suction chamber 105 in the form of a mist due to the vaporization of the working fluid in the oil. Therefore, this oil is easy to ride on the leakage flow in the compression chamber 100, and the sealing performance is further improved.

  On the other hand, the oil flowing into the back pressure chamber 110 from the orbiting bearing oil supply passage and the main bearing oil supply passage is agitated by the projections of the Oldham ring 5 and the orbiting scroll 3 moving in the back pressure chamber 110 and dissolved therein The gas rises rapidly by promoting gasification. As a result, the back pressure, which is the pressure in the back pressure chamber 110, becomes higher than the suction pressure, and attracting against the pulling force that pulls the orbiting scroll 3 away from the fixed scroll 2 by the compressed fluid in the compression chamber 100. A force can be quickly applied to the orbiting scroll 3. As a result, the orbiting scroll 3 is reliably pressed against the fixed scroll 2 not only during normal operation but also immediately after startup, and the compression operation is reliably and stably maintained.

  However, if the back pressure is too high, the urging force acting between the scrolls 2 and 3 increases, causing a reduction in compression performance due to sliding loss. For this reason, a back pressure chamber outflow passage 135 that connects the back pressure chamber 110 and the casing internal space connected to the oil storage portion 125 is provided for extracting oil and working fluid from the back pressure chamber 110 when the back pressure rises excessively. . In the middle of the outflow path 135, a back pressure control valve 26 is provided that opens when the difference between the back pressure and the suction pressure (pressure in the casing internal space) exceeds a predetermined value. The back pressure control valve 26 includes a compressed valve spring 26b, a valve plate 26c, and a valve cap 26d, and the predetermined value corresponds to the amount of compression of the valve spring 26b and is a substantially constant value. When this back pressure control is used as a compressor in an air-conditioning cycle, it can be used together with the above-described bypass valve 22 to achieve an optimal back pressure setting under a very wide range of operating conditions and to improve the compression performance. Play.

  As described above, the oil supply pump 30 boosts the oil and the working fluid dissolved therein to the back pressure, and then supplies the oil to the auxiliary bearing 25, the main bearing 24, the swivel bearing 23, the suction chamber 105, and the back pressure chamber 110. To play a role. The back pressure control valve 26 serves to discharge oil and working fluid from the back pressure chamber 110 to the space in the casing 8 while controlling the back pressure to be higher than the suction pressure by a predetermined value.

  As is apparent from the above description, the oil pump 30 also plays a role of boosting as well as the oil transfer, so that the pump work increases, and the improvement in the compression performance of the scroll compressor 1 includes the improvement in the performance of the oil pump 30. Especially important. Conventionally, a performance improvement measure that relies on the improvement of the shape and dimensional accuracy of the pump element is adopted.In this embodiment, a measure to improve the performance by pressing the pump elements against each other to reduce the seal gap and suppressing leakage. Adopted. Thereby, in this embodiment, the performance improvement of the oil supply pump 30 is implement | achieved, suppressing the increase in the processing cost accompanying the improvement of the shape and dimensional accuracy of a pump component.

  Next, the oil supply pump 30 which implement | achieves the above operations is demonstrated using FIG. 2A, FIG. 2B, and FIGS. 5 is a cross-sectional view taken along line LL in FIG. 2A, FIG. 6 is a plan view of a base plate 30d of the oil pump 30 in FIG. 2A, FIG. 7 is a perspective view of the inner rotor 30a of the oil pump 30 in FIG. 9 is a perspective view of the outer rotor 30b of the oil pump 30 of FIG. 2, FIG. 9 is an explanatory diagram of the pressure area of the bottom surfaces of both the rotors 30a and 30b in FIG. 2A, and FIG. 10 is an explanatory diagram of the pushing force applied to both the rotors 30a and 30b FIGS. 11A and 11B are explanatory diagrams of the discharge pressure region of the oil pump 30 in FIG. 2A.

  First, the configuration of the oil supply pump 30 will be described. The oil supply pump 30 is an internal gear pump that includes an inner rotor 30a that is an external gear and an outer rotor 30b that is an internal gear having one more tooth than the internal rotor.

  Unlike a normal inner rotor, the inner rotor 30a is integrally formed on the upper side surface of the inner rotor tooth profile portion 30a1 forming an external gear and the inner rotor tooth profile portion 30a1, and the upper side of the outer rotor 30b. It is an inner rotor with an end plate composed of an end plate portion 30a2 protruding to the surface side. The end plate portion 30a2 constitutes a cover that covers the upper side surface of the inner rotor tooth profile 30a1 (the boundary surface between the inner rotor tooth profile 30a1 and the end plate portion 30a2) and the upper side surface of the outer rotor 30b.

  The inner rotor 30a is attached to the oil supply pump shaft portion 6f protruding from the lower end of the crankshaft 6. Here, a D-shaped mounting hole 30i is provided in the inner rotor 30a so that the inner rotor 30a rotates integrally with the crankshaft 6, and a cut surface is provided in the oil pump shaft portion 6f (see FIGS. 5 and 7). ). The oil pump shaft portion 6f is formed to be thinner than the main shaft portion of the crankshaft 6 with a stepped portion. The upper surface of the inner rotor 30a comes into contact with this stepped portion.

  The other outer rotor 30b is mounted in the pump cylinder 30c integrated with the ball holder 25b so as to mesh with the inner rotor 30a, and is eccentric with respect to the center of the inner rotor 30a (center of the crankshaft 6). It is rotatably arranged at the position. The ball holder 25b and the pump cylinder 30c constitute a housing 40.

  And base plate 30d is arrange | positioned so that the lower side surface of both rotor 30a, 30b may be covered. The base plate 30d is disposed in close contact with the lower surface of the pump cylinder 30c and is fixed by bolts. The base plate 30d is formed with a pump suction groove 30e and a pump discharge groove 30f on a surface facing both the rotors 30a and 30b (see FIG. 6). A pump suction hole 30g which is a through hole is opened in the pump suction groove 30e.

  Since the pump suction groove 30e and the pump discharge groove 30f do not use the compression action due to the volume reduction of the pump chamber 140, the pump suction groove 30e and the pump discharge groove 30f have a shape having an elongated groove portion over the entire side of the expansion side and the reduction side of the pump chamber 140. To do. Therefore, it is necessary to align the pump chamber 140 with the pump suction groove 30e and the pump discharge groove 30f, and positioning holes 30h and 30i are provided in the base plate 30d and the pump cylinder 30c (ball holder 25b), respectively (FIGS. 6 and 6). 5), and the alignment reference for assembly. Here, each of the two positioning holes 30h and 30i is configured not to face each other by 180 degrees and to avoid an assembly error that reverses the suction side and the discharge side. The pump suction groove 30e and the pump discharge groove 30f may have a groove depth of a portion having a small groove width so that the flow velocity is as small as possible. For example, in the case of the pump discharge groove 30f, the oil concentrates on the central circular part 30f1, so that the groove depth of the connecting groove part 30f3 that connects the central circular part 30f1 and the surrounding crescent moon part 30f2 is increased toward the center. Thereby, since the maximum flow velocity of oil can be reduced, the pressure loss is reduced, and the performance of the oil supply pump is improved.

  Next, the operation of the oil supply pump 30 will be described. The rotation of the crankshaft 6 accompanying the operation of the scroll compressor 1 (the direction of the arrow in FIG. 5) rotates the inner rotor 30a, and the outer rotor 30b rotates accordingly. Accordingly, the plurality of pump chambers 140 shown in FIG. 5 separated by the engagement of the rotors 30a and 30b expands the volume on the pump suction groove 30e side, so that the oil in the oil storage section 125 is removed from the pump suction hole 30g. Inhale.

  The pump chamber 140 transfers oil to the oil supply vertical hole 6b in order to reduce the volume on the pump discharge groove 30f side. However, since the oil sent to the oil supply vertical hole 6b enters the back pressure chamber 110 through the main bearing 24 and the slewing bearing 23 and does not involve the restriction, the oil supply pump 30 supplies the suction pressure oil to the back pressure. Responsible for boosting pressure. That is, the oil supply pump 30 does not simply transfer the oil to the oil supply vertical hole 6b, but performs pressure-feeding with pressure increase.

  For this reason, if there is a gap in the side surfaces of both rotors 30a and 30b, leakage due to a pressure difference occurs from the discharge side, which is the back pressure, to the suction side of the suction pressure, and the capability of the oil supply pump 140 is reduced. As a conventional general countermeasure against this, either install a large-capacity oil pump with large energy consumption, or install a high-performance oil pump that suppresses leakage with a high-precision pump element that increases processing costs. Was considered. In the present embodiment, the former greatly reduces the energy efficiency of the scroll compressor. Therefore, in the present embodiment, the latter measure is further improved to suppress leakage and improve the performance of the oil pump. It was realized.

  A means for improving the oil pump performance while suppressing the processing cost increase will be described below. The basic guideline for the leakage suppression measure is to reduce the cross-sectional area of the leak channel, that is, to reduce the clearance of the elements constituting the leak channel. However, if the clearance is reduced too much, local interference between pump components may occur, leading to an increase in sliding loss, which may reduce the performance of the oil pump. For this reason, it is necessary to reduce the clearance without causing local interference between the pump components.

  In this embodiment, the end plate 30a2 is attached to the side surface of the inner rotor, which is a component of the oil pump 30, and the end plate is energized by the thrust force of the crankshaft 6 by biasing the inner rotor 30a. The part 30a2 is operated while being urged toward the outer rotor 30b. Here, as shown in FIG. 5, the outer edge of the end plate portion 30a2 is provided so as to cover the entire pump chamber 140 formed between the two rotors.

  Further, the thickness of the tooth profile of the outer rotor 30b (see FIG. 8) is made slightly thicker (see FIG. 2B) than the thickness of the tooth profile of the inner rotor 30a (see FIG. 7). In FIG. 2B, the clearance is illustrated with an emphasis for explanation, and the actual clearance level on the inner rotor side is about 10 to 100 μm.

  As a result, the upper rotor side surface of the outer rotor slides in close contact with the end plate 30a2, and the lower side surface of the outer rotor slides in close contact with the base plate 30d, so that the side clearance of the outer rotor 30b can be made substantially zero. Become. As a result, it is possible to greatly suppress leakage in the side clearance of the outer rotor 30b. Therefore, since the performance of the oil supply pump 30 is greatly improved without increasing the tooth profile accuracy of both the rotors 30a and 30b, the processing cost can be reduced and the energy efficiency of the scroll compressor 1 can be improved at the same time.

  Further, since the inner rotor 30a is sandwiched between the crankshaft 6 and the outer rotor 30b, and the outer rotor 30b is sandwiched between the end plate 30a2 and the base plate 30d of the inner rotor 30a, the axial positions of both the rotors 30a and 30b are determined. For this reason, it is possible to stabilize the performance of the oil supply pump and improve the oil supply reliability even under operating conditions in which the pressure fluctuations around the rotors 30a and 30b are large.

  Next, the biasing force of the inner rotor 30a to the outer rotor 30b will be described. Generally speaking, this urging force is obtained by dividing the surface of the crankshaft 6 and the rotor portions provided at the lower end thereof into one piece, and dividing the surface thereof into surface elements, and obtaining the normal vector (of the small surface element). The value obtained by multiplying the inner product of the upward unit vector in the direction of the crankshaft axis by the pressure of the portion is integrated over the entire surface.

  As is apparent from FIGS. 1 and 2, in the case of this embodiment, back pressure is applied to the entire upper portion of the crankshaft 6 with the main bearing 24 as a boundary, and the suction pressure is applied to the lower portion except for the bottom surfaces of both rotors. It depends. If the pressure reference is the suction pressure, in order for the inner rotor 30a to urge toward the outer rotor 30b side, the upper part from the suction pressure is defined as the following (Expression 1): (Expression 2) is required.

ΔP (p) ≡p− (suction pressure) (Formula 1)
ΔP (back pressure) × (Crankshaft main shaft cross-sectional area)>
(Force due to the pressure higher than the suction pressure of the bottom surfaces of the meshing rotors) (Equation 2)
In this case, the urging force is expressed by the following (Equation 3).

Energizing force = ΔP (back pressure) x (Crankshaft main shaft cross-sectional area)-
(Force due to pressure higher than the suction pressure of the bottom surfaces of the meshing rotors) (Equation 3)
Here, the force due to the pressure equal to or higher than the suction pressure of the bottom surfaces of the meshing rotors is expressed by the following (formula 4).

Force due to the pressure higher than the suction pressure on the bottom of the meshing rotors =
ΣΔP (p) × (pressure p region area) (Formula 4)
In order to obtain the urging force, as described above, the calculation of (Equation 4) is required. To calculate this precisely, an estimate of the pressure distribution on the bottom surfaces of both rotors and an integral calculation using the estimated value are required. It is necessary and extremely troublesome.

  Therefore, a simple calculation method of (Equation 4) described above is proposed below.

  First, a region where pressure is determined at the bottom surfaces of both meshing rotors is obtained. The case of this embodiment is shown in FIG. FIG. 9 is a view of the bottom surfaces of both rotors as viewed from below. The region where the oil discharged from the oil pump 30 exists (cross-hatched portion) is determined as a back pressure region, and the region where the suction oil of the oil pump 30 exists (one-way hatched portion) is determined as a suction pressure region. Here, although not clearly shown in FIG. 9, the outer peripheral portion of the outer rotor 30 b has a suction pressure. This is because the oil pump back space 145 has a gap between the ball bush 25a and the ball holder 25b (see FIG. 2A). The oil pump back space 145 is a space located on the upper side surface side of the oil pump 30 and is a space facing the end plate portion 30a2 in the present embodiment.

  Next, the pressure in the region where the pressure is not fixed (the region without hatching in FIG. 9) is estimated as follows. Considering a half line drawn from the center of the oil supply vertical hole 6b, which is the oil outlet from the oil supply pump 30, the intersection with the above-described pressure determination region is examined. Then, the midpoint of the line segment crossing the pressure undetermined region and the pressure deciding region at which both ends are different (R11 in the case of the half straight line R1, R22 in the case of the half straight line R2) is obtained, and the suction pressure is obtained. And the back pressure boundary. On the other hand, a line segment that crosses the pressure undetermined region and whose both ends are the same pressure determined region (R12 in the case of the half line R1, R21 in the case of the half line R2) is the same pressure region as the pressure at both ends. It is considered. By the procedure as described above, the pressure undetermined region is divided into a back pressure region and a suction pressure region.

  FIG. 10 shows the division situation in the present embodiment. The rough hatched portion in FIG. 10 is a region obtained by dividing the pressure undetermined region according to the above procedure, and the cross hatched portion is the back pressure region and the one-way hatched portion is the suction pressure region. As described above, as a result of being divided into the back pressure region and the suction region, (Equation 4) is simplified as follows and can be easily calculated.

Force due to the pressure higher than the suction pressure at the bottom of both meshing rotors = ΣΔP (p) × (pressure p area area)
= ΔP (back pressure) x (back pressure area) + ΔP (suction pressure) x (suction pressure area)
= ΔP (back pressure) x (back pressure area)
(∵ΔP (suction pressure) = 0) (Formula 4 ′)
By substituting (Equation 4 ′) into (Equation 2) and (Equation 3), a target energization determination formula and an energizing force calculation formula are derived.

(Crankshaft main shaft cross-sectional area)> (Back pressure area of both rotor bottom surfaces) (Formula 2 ')
Energizing force = ΔP (back pressure) x {(Crankshaft main shaft cross-sectional area)-
(Back pressure area at the bottom of both rotors)} (Formula 3 ′)
The energization determination of this embodiment is performed by (Equation 2 ′). The back pressure regions on the bottom surfaces of both rotors are the regions shown in FIG. 11 (this is a region where the fine cross-hatched portion and the rough cross-hatched portion in FIG. 8 are combined). It can be seen from the calculation that the area of this region is smaller than the cross-sectional area of the crankshaft main shaft. Therefore, the inner rotor 30a biases the outer rotor 30b and reduces the side clearance between the rotors 30a and 30b.

Further, the urging force can be obtained from (Equation 3 ′), but since the back pressure control valve 26 is used in this embodiment, ΔP (back pressure) in this equation is the value of the back pressure control valve 26. The predetermined value itself corresponds to the compression amount of the valve spring 26b. Therefore, by combining with the back pressure control method using the back pressure control valve 26, the urging force can always be secured at a constant value under any operating condition. For this reason, the inner rotor 30a can be stably urged to the outer rotor 30b under any operating condition, and the high performance of the oil pump 30 can be realized stably, so that the oil pump 30 is mounted. In addition to the high performance of the scroll compressor 1, high oil supply reliability can be realized.
(Second Embodiment)
Next, the scroll compressor of 2nd Embodiment of this invention is demonstrated using FIG. FIG. 12 is a cross-sectional view (a diagram corresponding to part M in FIG. 1) of the oil supply pump part in the scroll compressor according to the second embodiment of the present invention. The second embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment.

In the second embodiment, a cylinder penetrating horizontal path 25c, which is a communication path connecting the oil pump back space 145 and the oil storage part 125, is provided in the pump cylinder 30c. Since the pressure in the back surface space 145 of the oil pump is reliably held at the suction pressure by the cylinder through horizontal path 25c, the urging force of both the rotors 30a and 30b is stabilized, and the oil supply reliability is improved. Note that a communication path that connects the oil pump back space 145 and the oil storage part 125 may be provided in the ball holder 25b.
(Third embodiment)
Next, the scroll compressor of 3rd Embodiment of this invention is demonstrated using FIG. FIG. 13 is a cross-sectional view (a diagram corresponding to part M in FIG. 1) of the oil supply pump part in the scroll compressor according to the third embodiment of the present invention. The third embodiment is different from the second embodiment in the points described below, and the other points are the same as those in the second embodiment, and therefore, redundant description is omitted.

In the second embodiment, the oil feed pump back space 145 and the oil storage portion 125 are connected to the pump cylinder 30c, and the cylinder penetrating passage is a communication path in which the oil storage portion side opening is installed below the oil pump back space side opening. A ramp 25c is provided. The cylinder penetrating ramp 25c ensures that the pressure of the oil pump back space 145 is maintained at the suction pressure, and the oil reservoir 125 reaches a height above the opening on the oil reservoir side of the holder penetrating ramp 25d installed at a low position. Even if the oil level falls, the working fluid does not flow into the back plate space 145. Thereby, even if the oil level of the oil storage part 125 falls for some reason, there is an effect that the oil supply capability of the oil supply pump 30 is not lowered and the oil supply reliability is improved.
(Fourth embodiment)
Next, the scroll compressor of 4th Embodiment of this invention is demonstrated using FIG. FIG. 14 is a cross-sectional view (a diagram corresponding to part M in FIG. 1) of the oil supply pump part in the scroll compressor according to the fourth embodiment of the present invention. The fourth embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment.

  In the fourth embodiment, the auxiliary bearing oil supply passage is provided with an auxiliary bearing oil supply groove 6h that connects the auxiliary bearing oil supply lateral hole 6g and the oil supply pump back space 145 and has substantially no throttle action. In other words, the auxiliary bearing oil supply lateral hole 6g and the auxiliary bearing oil supply groove 6h form a communication path between the oil supply hole 6b of the crankshaft 6 and the oil pump back space 145. This communication path is formed by an oil supply path that does not substantially have a throttling action.

  With this configuration, the pressure of the oil pump back space 145 is reliably maintained at the back pressure (suction pressure + predetermined constant value), so that the oil supply groove serves as a back pressure introduction path. When the reference pressure is considered as the back pressure, the biasing force always takes a value obtained by applying the back pressure to the area of the suction pressure region on the bottom surfaces of the rotors 30a and 30b, and any design of the crankshaft 6 or the oil pump 30 is applied. In this case, both rotors 30a and 30b can be reliably energized, and there is an effect that the oil supply reliability is improved.

  Furthermore, the ball bush 25a is pushed upward by the pressure of the oil pump back space 145 and is in close contact with the ball holder 25b. As a result, the central annular portion that supports the crankshaft 6 is fixed, and the crankshaft 6 is stably supported, so that the reliability of the bearing portion is improved and the reliability of the scroll compressor 1 is improved. effective. Further, the friction coefficient at the bearing portion is also reduced, and there is an effect that the scroll compressor 1 having high energy efficiency can be realized.

Here, by installing the auxiliary bearing oil supply lateral hole 6g in the lower part of the auxiliary bearing 25, a wide range of oil supply of the auxiliary bearing 25 is reliably performed with a differential pressure, and bearing reliability is ensured. Further, instead of installing the auxiliary bearing oil supply groove 6h, the auxiliary bearing oil supply lateral hole 6g may be lowered to a position facing the lower side of the auxiliary bearing 25. Thereby, there exists an effect which can suppress processing cost.
(Fifth embodiment)
Next, the scroll compressor of 5th Embodiment of this invention is demonstrated using FIG.15 and FIG.16. FIG. 15 is an assembly perspective view of an inner rotor of an oil supply pump portion in a scroll compressor according to a fifth embodiment of the present invention, and FIG. 16 is a plan view of the inner rotor of FIG. The fifth embodiment is different from the first to fourth embodiments in the following points, and the other points are the same as those in the first to fourth embodiments. .

  In the fifth embodiment, the inner rotor 30a is divided into an inner rotor tooth profile 30a1 and a separate end plate 30a3, and is formed by a combination of connecting screws 30a4. The end plate 30a3 is provided with a mounting hole 30i3 having the same D shape as the mounting hole 30i2 of the inner rotor tooth profile 30a1. The inner rotor 30a is divided into a separate end plate 30a3 and a columnar inner rotor tooth profile 30a1, and the inner rotor tooth profile 30a1 having a complicated shape is formed into a column shape that can be processed by sintering, casting, extrusion molding, or the like. . Thereby, reduction of the processing cost of the oil supply pump 30 can be aimed at. Further, a method is adopted in which the inner rotor tooth profile 30a1 is first processed into a long rod shape by sintering, casting, extrusion molding, or the like, and then cut into a regular length. Thereby, processing efficiency improves further and the processing cost of the oil supply pump 30 reduces. From the above, there is an effect that the processing cost of the oil supply pump 30 is reduced, and further, the processing cost of the scroll compressor 1 on which the oil supply pump 30 is mounted is reduced.

  The separate end plate 30a3 and the inner rotor tooth profile 30a1 are sequentially inserted into the oil pump shaft 6f of the crankshaft 6 without fixing the separate end plate 30a3 and the inner rotor tooth profile 30a1 with a connecting screw. Even if it only does, the seal between the step part of the crankshaft 6, the end plate 30a3, and the outer rotor 30b can be ensured by the thrust force of the crankshaft 6, and the cost can be further reduced.

Further, if the crankshaft 6 is dimensioned to cover the entire pump chamber 140, and the step serves as a cover, the end plate can be omitted, and the cost can be further reduced.
(Sixth embodiment)
Next, the scroll compressor of 6th Embodiment of this invention is demonstrated using FIG. FIG. 17 is an assembly perspective view of an inner rotor of an oil supply pump portion in a scroll compressor according to a sixth embodiment of the present invention. The sixth embodiment is different from the fifth embodiment in the following points, and the other points are the same as those in the fifth embodiment.

In the sixth embodiment, the inner rotor tooth profile 30a5 separated from the end plate 30a3 has a mounting hole 30i5 to the oil supply pump shaft 6f provided at the center thereof changed from a D-shaped hole to a circular hole. is there. According to the inner rotor tooth profile 30a5, processing is easier than in the case of providing a D-shaped hole, and the processing cost can be further reduced. Thereby, there exists an effect that the processing cost of the oil supply pump 30 is reduced, and further, the processing cost of the scroll compressor 1 on which this is mounted is reduced.
(Seventh embodiment)
Next, the scroll compressor of 7th Embodiment of this invention is demonstrated using FIG. FIG. 18 is an assembly perspective view of an inner rotor of an oil supply pump portion in a scroll compressor according to a seventh embodiment of the present invention. The seventh embodiment is different from the fifth embodiment in the following points, and the other points are the same as those in the fifth embodiment.

In the seventh embodiment, the end plate 30a6 separated from the inner rotor tooth profile 30a2 has a mounting hole 30i6 to the oil pump shaft 6f provided at the center thereof changed from a D-shaped hole to a circular hole. is there. According to the end plate 30a6, processing is easier than in the case of providing a D-shaped hole, and the processing cost can be further reduced. Thereby, there exists an effect that the processing cost of the oil supply pump 30 is reduced, and further, the processing cost of the scroll compressor 1 on which this is mounted is reduced.
(Eighth embodiment)
Next, the scroll compressor of 8th Embodiment of this invention is demonstrated using FIG. FIG. 19 is an enlarged view of a main part of an oil supply pump portion in a scroll compressor according to an eighth embodiment of the present invention. The eighth embodiment is different from the first embodiment in the points described below, and the other points are the same as those in the first embodiment, and therefore, redundant description is omitted.

In the eighth embodiment, the tooth profile thickness of both rotors 30a, 30b of the oil supply pump 30 is set so that the inner rotor side is thicker than the outer rotor side. As a result, the lower side surface side of the inner rotor 30a slides in close contact with the base plate 30d. By the way, the axial position of the outer rotor 30b is not fixed (it is between the upper end plate 30a2 and the lower base plate 30d, but it is not determined where in between), the side clearance of the outer rotor 30b is The upper side clearance and the lower side clearance are divided. Even if the total clearance is the same, dividing the clearance reduces leakage. As described above, the side clearance of the inner rotor 30a can be substantially zero, and the side clearance of the outer rotor 30b can be divided into two parts by not determining the axial position of the outer rotor 30b. Leakage can be suppressed. Therefore, there is an effect that the performance of the oil supply pump 30 is improved, and consequently, the energy efficiency of the scroll compressor 1 on which the oil supply pump 30 is mounted can be improved.
(Ninth embodiment)
Next, the scroll compressor of 9th Embodiment of this invention is demonstrated using FIGS. 20-22. FIG. 20 is a longitudinal sectional view of the inner rotor or outer rotor used in the oil supply pump section of the scroll compressor according to the ninth embodiment of the present invention (a diagram corresponding to the 30aV plane section of FIG. 5 or the 30bV plane section of FIG. 6), 21 is a cross-sectional view of the inner rotor or outer rotor in the ninth embodiment (corresponding to the 30aH plane cross section of FIG. 5 or the 30bH plane cross section of FIG. 6), and FIG. 22 is the inner rotor and outer rotor of FIGS. It is a longitudinal cross-sectional view of the state which incorporated in the oil supply pump. The ninth embodiment is different from the first to eighth embodiments in the following points, and the other points are the same as those in the first to eighth embodiments. .

  In the ninth embodiment, an inner conforming film 30a7 is provided on the side surface, end plate surface, and tooth profile surface of the inner rotor 30a, or an outer conforming film 30b7 is provided on the side surface and tooth profile surface of the outer rotor 30b. In the side portions of the rotors 30a and 30b on which the urging force acts, the conformal coatings 30a7 and 30b7 are moderately worn to improve the shape error and surface roughness caused by machining during manufacture, and the side portions. Leakage is suppressed, the coefficient of friction between the surfaces on which the urging force acts is reduced, and the sliding loss is reduced. As a result, there is an effect that the performance of the oil supply pump 30 is improved, and consequently, the energy efficiency of the scroll compressor 1 on which the oil supply pump 30 is mounted can be improved. Further, this shape correction effect may be used to lower the processing accuracy to reduce the processing cost.

  In addition, as described in the first embodiment and the eighth embodiment, clearance is generated on the side surface due to the relationship between the thicknesses of the tooth profile portions of the outer rotor 30b and the inner rotor 30a. The clearance is reduced because the part that slides tightly wears out. Therefore, there is an effect that leakage on the side surface is suppressed in the entire region, and the performance of the oil supply pump is improved.

  Further, since the conformal coating is provided on the tooth profile surface, the interference portion is worn so as to avoid the interference generated by the meshing of the two rotors. As a result, the rotational center shift of both rotors caused by interference is suppressed, the clearance of the tooth profile portion is reduced, and leakage can be suppressed. At the same time, there is an effect that noise and vibration accompanying meshing are reduced.

  Furthermore, when this film is manufactured by a method of immersing the material so as to modify the surface of the material, it is not necessary to provide a manufacturing cost because masking is unnecessary when the film is provided on the entire surface. is there.

  It is to be noted that the same function can be achieved even if the conforming film is provided on the surface of the crankshaft 6, particularly on the step portion to the oil supply pump shaft portion 6f. Alternatively, a conforming film may be provided on the inner surface of the pump cylinder 30c and the upper surface of the base plate 30d.

Further, since the back pressure control valve 26 constantly increases the pressure (back pressure) in the back pressure chamber 110 by a constant value from the suction pressure, the shaft thrust force is always constant. Therefore, the deformation on the side surface of the pump element is always constant and settles to an optimum side shape by fitting, so that the pump performance can be greatly improved.
(10th Embodiment)
Next, a scroll compressor according to a tenth embodiment of the present invention will be described with reference to FIG. FIG. 23 is a plan view of a base plate of an oil supply pump in a scroll compressor according to a tenth embodiment of the present invention. The tenth embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment, and thus redundant description is omitted.

In this heat exchanger 10 embodiment, the suction groove and the discharge groove have a wedge shape (pump suction wedge groove 30e4, wedge groove 30f4). Since the pump suction groove 30e4 or the pump discharge groove 30f4 covers almost the entire surface of the pump chamber 140, the flow path cross-sectional area from the pump chamber 140, which is a complicated flow location, to the pump suction groove 30e4 or the pump discharge groove 30f4 increases. The flow resistance is reduced, unnecessary pressure boosting is avoided, and invalid work is reduced. As a result, there is an effect that the power consumption of the oil supply pump 30 is reduced, and that the energy efficiency of the scroll compressor 1 on which the oil supply pump 30 is mounted can be improved.
(Eleventh embodiment)
Next, a scroll compressor according to an eleventh embodiment of the present invention will be described with reference to FIG. FIG. 24 is a longitudinal sectional view (corresponding to FIG. 3) near the upper end portion of the crankshaft in the scroll compressor according to the eleventh embodiment of the present invention. The eleventh embodiment is different from the first embodiment in the points described below, and the other points are the same as those in the first embodiment, and thus redundant description is omitted.

In the eleventh embodiment, the upper end of the oil supply vertical hole 6b is roughly closed with an oil supply vertical hole plug 6j, a swirling oil horizontal hole 6i is provided below the swivel bearing groove 6e to communicate with the oil supply vertical hole 6b, and the back pressure chamber 110 side is sealed. is doing. As a result, the oil supplied to the slewing bearing 23 supplies the suction chamber 105, so that the amount of oil sent out by the oil supply pump 30 can be reduced. As a result, there is an effect that the power consumption of the oil supply pump 30 is reduced, and that the energy efficiency of the scroll compressor 1 on which the oil supply pump 30 is mounted can be improved.
(Twelfth embodiment)
Next, the scroll compressor of 12th Embodiment of this invention is demonstrated using FIG. FIG. 25 is an enlarged sectional view of the main portion of the suction chamber refueling in the vicinity of both scroll urging portions in the scroll compressor according to the twelfth embodiment of the present invention (a view corresponding to portion P in FIG. 1). The twelfth embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment, and thus redundant description is omitted.

In the twelfth embodiment, as the suction chamber oil supply passage 130, the suction chamber oil supply passage 2 g that connects the back pressure chamber 110 and the suction chamber 105 with a throttle is attached to the mounting portion 2 c that slides with the revolving end plate 3 b with the fixed scroll 2. Provided. As a result, the oil flowing into the back pressure chamber 110 supplies the suction chamber 105, so that the amount of oil sent out by the oil supply pump 30 can be reduced. As a result, there is an effect that the power consumption of the oil supply pump is reduced, and the energy efficiency of the scroll compressor 1 on which the oil supply pump is mounted can be improved.
(13th Embodiment)
Next, the scroll compressor of 13th Embodiment of this invention is demonstrated using FIG. FIG. 26 is a plan view of the orbiting scroll in the scroll compressor according to the thirteenth embodiment of the present invention. The thirteenth embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment, and thus redundant description is omitted.

In the thirteenth embodiment, there is provided a compression chamber oil supply passage 150 (formed by the end plate horizontal hole 3c and the compression chamber pore 3f) that supplies oil to the compression chamber 100 instead of the suction chamber 105. Thus, the pressurized oil can be used to ensure the sealing performance of the compression chamber 100 without reducing the pressure to the suction pressure. Therefore, since the energy used for boosting the oil can be effectively used, the energy efficiency of the scroll compressor 1 can be improved.
(14th Embodiment)
Next, a scroll compressor according to a fourteenth embodiment of the present invention is described with reference to FIG. FIG. 27 is a longitudinal sectional view (a view corresponding to part M in FIG. 1) of the oil supply pump part in the scroll compressor according to the fourteenth embodiment of the present invention. The fourteenth embodiment is different from the first embodiment in the following points, and the other points are the same as those in the first embodiment, and thus redundant description is omitted.

  In the fourteenth embodiment, an end plate back surface regulating portion 30c1 formed by a stepped portion of the pump cylinder 30c is provided on the back side of the inner rotor 30a. The clearance between the end plate 30a2 and the end plate back surface regulating portion 30c1 is about 50 μm to 100 μm. As a result, even if the urging force applied to the inner rotor 30a is insufficient due to an unforeseen cause and the rotors 30a and 30b are separated from each other, the axial position of the end plate 30a1 is defined by the end plate back surface regulating portion 30c1, An extreme decrease in the capacity of the oil pump 30 can be avoided. Therefore, there is an effect that the oil supply reliability of the oil supply pump 30 can be ensured, and further, the reliability of the scroll compressor 1 equipped with the oil supply pump can be ensured.

It is a longitudinal section of the scroll compressor concerning a 1st embodiment of the present invention. It is a detailed enlarged view of the M section in FIG. It is a principal part enlarged view of FIG. 2A. FIG. 2 is a detailed enlarged view of a portion N in FIG. 1. It is a top view of the turning scroll of FIG. It is LL sectional drawing of FIG. 2A. It is a top view of the base plate of the oil pump of FIG. 2A. It is a perspective view of the inner rotor of the oil supply pump of FIG. 2A. It is a perspective view of the outer rotor of the oil pump of FIG. 2A. It is explanatory drawing of the pressure range of the bottom face of both the rotors of FIG. 2A. It is explanatory drawing of the raising force concerning both rotors of FIG. 2A. It is explanatory drawing of the discharge pressure area | region of the oil supply pump 30 of FIG. 2A. It is sectional drawing of the oil supply pump part in the scroll compressor of 2nd Embodiment of this invention. It is sectional drawing of the oil supply pump part in the scroll compressor of 3rd Embodiment of this invention. It is sectional drawing of the oil supply pump part in the scroll compressor of 4th Embodiment of this invention. It is an inner rotor assembly perspective view of the oil supply pump part in the scroll compressor of a 5th embodiment of the present invention. FIG. 16 is a plan view of the inner rotor in FIG. 15. It is an inner rotor assembly perspective view of the oil supply pump part in the scroll compressor of a 6th embodiment of the present invention. It is an inner rotor assembly perspective view of the oil supply pump part in the scroll compressor of a 7th embodiment of the present invention. It is a principal part enlarged view of the oil supply pump part in the scroll compressor of 8th Embodiment of this invention. It is a longitudinal cross-sectional view of the inner rotor or outer rotor used for the oil supply pump part in the scroll compressor of 9th Embodiment of this invention. It is a cross-sectional view of the inner rotor or the outer rotor in the ninth embodiment. It is a longitudinal cross-sectional view of the state which assembled the inner rotor and outer rotor of FIG.20 and FIG.21 in the oil supply pump. It is a top view of the baseplate of the oil supply pump in the scroll compressor of 10th Embodiment of this invention. It is a longitudinal cross-sectional view near the upper end part of the crankshaft in the scroll compressor of 11th Embodiment of this invention. It is an expanded sectional view of the suction chamber oil supply main part in the vicinity of both scroll urging parts in the scroll compressor of a 12th embodiment of the present invention. It is a top view of the turning scroll in the scroll compressor of 13th Embodiment of this invention. It is a longitudinal cross-sectional view of the oil supply pump part in the scroll compressor of 14th Embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Scroll compressor, 2 ... Fixed scroll, 2a ... Fixed spiral body, 2b ... Fixed end plate, 3 ... Revolving scroll, 3a ... Revolving swirl body, 3b ... Revolving end plate, 3c ... End plate side hole, 3d ... Suction chamber pore, 3f ... compression chamber pores, 4 ... frame, 5 ... Oldham ring, 6 ... crankshaft, 6a ... pin part, 6b ... oil supply vertical hole (oil supply hole), 6c ... main bearing oil supply lateral hole, 6d ... main bearing groove, 6e ... Slewing bearing groove, 6f ... oil supply pump shaft, 6g ... sub-bearing oil supply lateral hole, 7 ... motor, 8 ... casing, 8a ... cylinder casing, 8b ... upper casing, 8c ... bottom casing, 10 ... compressor part, 22 ... bypass Valve, 23 ... Slewing bearing, 24 ... Main bearing, 25 ... Sub-bearing, 26 ... Back pressure control valve, 30 ... Oil pump, 30a ... Inner rotor, 30a1 ... Inner rotor tooth profile, 30a2 ... End plate (cover) , 30a3 ... end plate (cover), 30a7 ... inner conforming film, 30b ... outer rotor, 30b7 ... outer conforming film, 30c ... pump cylinder, 30c1 ... end plate rear surface regulating portion, 30d ... base plate, 30e ... pump suction groove, 30f DESCRIPTION OF SYMBOLS ... Pump discharge groove, 100 ... Compression chamber, 105 ... Suction chamber, 110 ... Back pressure chamber, 115 ... Swivel bearing chamber, 120 ... Discharge chamber, 125 ... Oil storage part, 130 ... Suction chamber oil supply path, 135 ... Back pressure chamber outflow 140, pump chamber, 145, oil pump back space, 150, compression chamber oil passage.

Claims (11)

A compressor section that compresses the working fluid; a crankshaft that drives the compressor section; a bearing that supports the crankshaft; and an oil supply pump that has an inner rotor and an outer rotor and supplies oil to the bearing. A casing housing the compressor unit, the crankshaft and the oil pump,
The casing is provided with an oil storage part for storing the oil in the internal space, while setting the internal space to the suction pressure,
The compressor part is formed by meshing the fixed scroll having the end plate and the spiral body standing on the end plate, the orbiting scroll having the end plate and the spiral body standing on the end plate, and reducing the volume. A compression chamber for compressing the working fluid, and a back pressure chamber provided on the back surface of the orbiting scroll and serving as an intermediate pressure space higher than the suction pressure and lower than the discharge pressure,
The crankshaft is rotationally driven by a rotational drive source to rotationally drive the orbiting scroll, and includes an oil supply hole serving as an oil supply passage to the bearing,
In the scroll compressor provided at the end of the crankshaft on the side opposite to the orbiting scroll so as to pressurize the oil in the oil storage section and supply the oil to the back pressure chamber through the oil supply hole of the crankshaft and the bearing. ,
The oil pump urges a cover covering the side surfaces of the inner rotor and the outer rotor to at least one of the side surface of the inner rotor and the side surface of the outer rotor by a thrust force of the crankshaft. A scroll compressor characterized by being provided in the above.   2. The oil pump according to claim 1, wherein the oil pump covers the inner rotor, the outer rotor, a pump cylinder disposed around the outer rotor, and a side surface of the inner rotor and the outer rotor on the side of the anti-compressor part. A scroll compressor comprising an internal gear type pump comprising a base plate and the cover covering a side surface of the inner rotor and the outer rotor on the compressor portion side.   3. The scroll compressor according to claim 2, wherein the cover is provided integrally with the tooth profile portion of the inner rotor or the tooth profile portion of the outer rotor.   3. The crankshaft according to claim 2, wherein the crankshaft has an oil pump shaft portion having a small diameter through a step portion at an end on the side opposite to the compressor portion, and the inner rotor is installed around the oil pump shaft portion. The scroll compressor is characterized in that the cover is sandwiched between a step portion of the crankshaft and at least one of the side surface of the inner rotor and the side surface of the outer rotor.   3. The crankshaft according to claim 2, wherein the crankshaft has an oil pump shaft portion having a small diameter through a step portion at an end on the side opposite to the compressor portion, and the inner rotor is installed around the oil pump shaft portion. The cover is formed as a separate member from the inner rotor and the outer rotor, and between the step portion of the crankshaft and at least one of the side surface of the inner rotor and the side surface of the outer rotor. A scroll compressor characterized by being sandwiched between the two.   In Claim 2, Along with the crankshaft, the compressor part, the motor used as the rotation drive source, and the oil pump are attached to the crankshaft in this order, and the bearing is arranged on the compressor part side of the motor. A main bearing and a sub-bearing disposed on the anti-compressor part side of the motor, the sub-bearing and the oil pump are disposed adjacent to each other, and the sub-bearing includes a bearing bush and a bearing holder for holding the bearing bush. A scroll compressor, wherein the bearing holder and the pump casing are fixedly arranged or integrally formed to form a housing.   In Claim 6, The said housing is provided with the communicating path which connects the oil pump back space formed in the inner surface of the said housing between the said oil pump and the said bearing holder, and the said oil storage part space. A scroll compressor characterized by that.   8. The scroll compressor according to claim 7, wherein the communication passage is provided with an opening on the oil storage space side lower than an opening on the back surface space side of the oil pump.   In Claim 6, the said crankshaft provided the back pressure introduction path which connects the oil pump back space formed in the inner surface of the said housing between the said oil pump and a bearing holder, and the said oil hole. A scroll compressor characterized by that.   The scroll compressor according to claim 1, wherein a conforming film is formed on at least one surface that receives a thrust force of the cover, the inner rotor, and the outer rotor.   2. The scroll compressor according to claim 1, further comprising back pressure control means for making the pressure in the back pressure chamber higher than the suction pressure by a substantially constant value.

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