JP6545922B1 - Rolling cylinder positive displacement compressor - Google Patents

Abstract

The rolling cylinder positive displacement compressor according to the present invention comprises a cylindrical rolling cylinder having a cylinder groove, a swing piston having a slide groove, a stationary cylinder, a pin mechanism, a drive source, a rolling cylinder and a drive source. A drive transmission unit to be connected, and a casing that houses a pivot piston, a rolling cylinder, a stationary cylinder, a pin mechanism, a drive source and a drive transmission unit, and the pivot piston, the rolling cylinder and the stationary cylinder constitute a compression unit, and a pin The mechanism is inserted into the slide groove, and the swinging piston reciprocates relative to the cylinder groove, and a suction chamber, a compression chamber and a discharge chamber are formed in the compression section by the reciprocation. The drive source drives at least the rolling cylinder through the drive transmission unit. As a result, in the rolling cylinder positive displacement compressor, it is possible to reduce the collision between the movable compression elements and to suppress the deterioration of the performance as the compressor.

Description

  The present invention relates to a rolling cylinder positive displacement compressor.

  The rolling cylinder positive displacement compressor having a fixed pin mechanism has a geometry in which two chords drawn from either point on a circle passing through the center of the pin mechanism and the rolling cylinder rotation center have an angle. It is a unique device that makes use of the scientific relationship (constant angle law). In this device, as a compression element which constitutes a compression chamber for compressing a working fluid such as a refrigerant, there are a stationary cylinder which is a stationary compression element which does not move and a movable compression element which moves with motion. Movable compression elements include a rolling cylinder that rotates and a pivoting piston that has a pivoting motion centered on a circle passing through the center of the rolling cylinder and pin mechanism and that is oriented toward the center of the rolling cylinder.

  In order to cooperate to form a compression chamber, these movable compression elements exert forces with each other by sliding or the like, and the compression of the working fluid exerts a force from the working fluid and supports of the respective compression elements. Since the force acting in the direction from the working fluid to prevent the pivoting motion acts on the pivoting piston, a driving force to counter it is essential. On the other hand, the rolling cylinder is characterized in that the torque that hinders the rotational movement from the working fluid does not work.

  In Patent Document 1, driving force is applied to the orbiting piston by a shaft that the motor rotationally drives, and compression of the working fluid is realized by opposing the force acting on the orbiting piston from the working fluid, and driving force is applied to the rolling cylinder. The configuration not given is described.

International Publication No. 2016/067355

  As described in Patent Document 1, the torque acting on the rolling cylinder is only the friction torque acting from the support and the torque acting from the orbiting piston.

  By the way, since there is always a gap in the sliding portion between the turning piston and the rolling cylinder, the rotation angle of the rolling cylinder that cooperates to form the compression chamber is one, even when the turning piston is at a position where it is There is always a range (rotation) of rotation angles that can be incorporated.

  For this reason, the rolling cylinder always lowers its rotational speed due to the above-mentioned friction torque, shifts to the smaller rotation angle within the range of rattling, and finally collides with the swing piston at the sliding portion.

  Since a large torque from the working fluid does not act on the rolling cylinder, the collision makes a rapid jump to the larger rotation angle in the range of rattling. Then repeat the same collision. Furthermore, if this collision becomes extremely intense, a collision with the orbiting piston will occur even when returning to a position where the rotation angle is large, and a more severe collision will occur in an extremely short cycle.

  As a result, there is a decrease in reliability due to vibration noise and wear of the sliding portion, an increase in sliding loss due to generation of a large impact load in the sliding portion, and an increase in leakage loss due to oil film formation failure due to instability of the sealing portion of the sliding portion. As a result, there is a problem that the compressor performance is lowered.

  An object of the present invention is, in a rolling cylinder type positive displacement compressor, to reduce collisions between movable compression elements and to suppress a decrease in performance as a compressor.

  The rolling cylinder positive displacement compressor according to the present invention comprises a cylindrical rolling cylinder having a cylinder groove, a swing piston having a slide groove, a stationary cylinder, a pin mechanism, a drive source, a rolling cylinder and a drive source. A drive transmission unit to be connected, and a casing that houses a swing piston, a rolling cylinder, a stationary cylinder, a pin mechanism, a drive source and a drive transfer unit, and the swing piston, the rolling cylinder and the stationary cylinder constitute a compression unit, and a pin The mechanism is inserted into the slide groove, and the swinging piston reciprocates relative to the cylinder groove, and a suction chamber, a compression chamber and a discharge chamber are formed in the compression section by the reciprocation. The drive source drives at least the rolling cylinder via the drive transmission unit.

  According to the present invention, in the rolling cylinder positive displacement compressor, the collision between the movable compression elements can be reduced, and the deterioration of the performance as the compressor can be suppressed.

FIG. 1 is a longitudinal sectional view showing an RC compressor according to a first embodiment. FIG. 1 is a perspective view showing a rolling cylinder of an RC compressor according to a first embodiment. FIG. 2 is a perspective view showing a swing piston of the RC compressor according to the first embodiment. FIG. 1 is a perspective view showing a pin mechanism of an RC compressor according to a first embodiment. 5 is a perspective view showing another pin mechanism of the RC compressor according to Embodiment 1. FIG. FIG. 2 is a flowchart showing a compression process of the RC compressor according to the first embodiment. FIG. 2 is an exploded perspective view showing an oil supply pump of the RC compressor according to the first embodiment. FIG. 7 is a longitudinal sectional view showing an RC compressor according to a second embodiment. It is the L section enlarged view of FIG. FIG. 6 is a perspective view of a rolling cylinder of the RC compressor according to a second embodiment as viewed from above. FIG. 6 is a perspective view of a rolling cylinder of the RC compressor according to a second embodiment as viewed from below. FIG. 6 is a perspective view showing a swing piston of the RC compressor according to a second embodiment. FIG. 7 is a perspective view showing a pin mechanism of an RC compressor according to a second embodiment. It is the schematic diagram which looked at the shaft collar part and rolling cylinder contact part of RC compressor which concern on Example 2 from the lower side of a shaft. FIG. 10 is a perspective view showing a rolling cylinder of an RC compressor according to a third embodiment. FIG. 1 is a cross-sectional view showing an oil supply pump of an RC compressor according to a first embodiment. FIG. 14 is an exploded perspective view showing a refueling pump of an RC compressor according to a fourth embodiment.

  The present invention relates to a rolling cylinder positive displacement compressor having a fixed pin mechanism that defines the attitude of a pivoting piston.

  Hereinafter, a rolling cylinder positive displacement compressor (hereinafter also referred to as “RC compressor”) of the present invention will be described in detail with reference to the drawings, using a plurality of embodiments. The same parts in the respective embodiments will be described using the same drawings. In addition, the same reference numerals in the drawings of the respective embodiments indicate the same or equivalent parts, and duplicate explanations will be omitted. In addition, the dimensional ratio of each element to show in figure has shown one Embodiment. Therefore, the size relationship and angle of each dimension in the illustrated shape also show an embodiment. Further, in the drawings, the parenthesized reference numerals indicate modified embodiments by adding or removing. In the latter case, addition or removal is stated in the text. The specific dimension value is not particularly limited, but it is desirable that the outer diameter of the rolling cylinder positive displacement compressor be in the range of 10 mm to 2000 mm.

  The RC compressor according to the first embodiment will be described with reference to FIGS. 1 to 6 and 15.

  The present embodiment for rotationally driving the rolling cylinder is an RC compressor of a type in which a slider is provided in a pin mechanism which is a support portion of a swing piston and a piston drive source which is a drive source of the swing piston is not provided.

  FIG. 1 shows the overall configuration of the RC compressor according to the first embodiment. In the description of this figure, the configuration described in Patent Document 1 is simplified.

  As shown in the drawing, the RC compressor is roughly divided into a compression unit, a motor 7 as a driving source, and an oil storage unit 125.

  In the figure, in the casing constituted by the casing cylindrical portion 8a, the upper casing lid 8b and the lower casing lid 8c, there are provided a compression unit, the motor 7 serving as a drive source of the compression unit therebelow, and the compression unit A shaft 6 which is a drive transmission unit connecting the motor 7 is disposed. The shaft 6 is arranged in the vertical direction.

  The compression section includes a rolling cylinder 1, a pivot piston 3 and a stationary cylinder 2 as components acting directly on the working fluid to be compressed. The rolling cylinder 1 and the pivoting piston 3 are movable compression elements. The stationary cylinder 2 is also a stationary compression element. The movable and stationary compression elements form a working chamber. The working chamber is repeatedly switched to the suction chamber 95, the compression chamber 100, and the discharge chamber 105 during operation of the RC compressor.

  With regard to these materials, if the orbiting piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of cast iron, the cost can be reduced. Alternatively, the rolling cylinder 1 may be made of an aluminum alloy, and the orbiting piston 3 and the stationary cylinder 2 may be made of cast iron. In this way, since the weight of the rolling cylinder 1 that rotates passively can be reduced, it is possible to make it difficult to cause an operation failure and to make the operation smooth. Furthermore, if all of the orbiting piston 3, the rolling cylinder 1 and the stationary cylinder 2 are made of aluminum alloy, the weight of the entire RC compressor can be reduced.

  The compression part is configured such that the upper part is covered by the stationary cylinder 2 and the lower part is covered by the frame 4. The compression portion is fixed to the cylindrical casing portion 8a by welding or the like. The frame 4 is provided with a main bearing 24 consisting of an upper main bearing 24a and a lower main bearing 24b. The shaft 6 is rotatably supported by the main bearing 24. The frame 4 supports the shaft 6. The shaft 6 projects downward from the frame 4. The stationary cylinder 2 is fixed to the frame 4 by a cylinder bolt 90.

  The stationary cylinder 2 is provided with a circular cylinder hole 2 b whose center axis is the cylinder rotation axis. The stationary cylinder 2 also has a cylinder outer peripheral groove 2m on the outer peripheral side surface thereof. From the upper surface of the stationary cylinder 2 is provided a bypass hole 2e penetrating to the cylinder hole 2b. A pin mechanism 5 is provided on the bottom of the cylinder hole 2b. A bypass valve 22 is provided on the upper surface side of the stationary cylinder 2.

  A discharge cover 230 is fixedly disposed on the upper portion of the stationary cylinder 2. The discharge cover 230 has a discharge cover plate 230b. The working fluid is configured to pass through the discharge cover chamber 130 which is a space between the upper surface of the stationary cylinder 2 and the discharge cover plate 230b, and to be spouted from the discharge cover port 230a into the swirl chamber 140 as a swirling flow. There is.

  The swing piston 3 is provided with a slide groove 3 b. The pin mechanism 5 is inserted into the slide groove 3b. In addition, the orbiting piston 3 is provided with a piston lower surface hole 3g. The pin mechanism 5 is fitted in the slide groove 3 b of the orbiting piston 3 and serves as a support that regulates the position and attitude of the orbiting piston 3.

  The motor 7 is composed of a rotor 7a fixed to the shaft 6 and a stator 7b fixed to the cylindrical casing 8a. Here, the rotor 7a attached to the shaft 6 is attached to the stator 7b forming the motor 7 by slightly lowering. This gives the shaft 6 an upward axial thrust.

  The oil storage portion 125 is a region surrounded by the casing cylindrical portion 8 a, the casing lower lid 8 c and the sub frame 35.

  At the lower end of the shaft 6, an oil supply pump 200 having a pressure increase capability is provided. The shaft 6 is provided with a shaft oil supply vertical hole 6 b (oil supply passage) penetrating the center in the central axis direction. Further, the shaft 6 is provided with oil supply horizontal holes (shaft oil supply auxiliary horizontal hole 6g, shaft oil supply lower main bearing hole 6f, shaft oil supply upper main bearing hole 6e) connected to the auxiliary bearing 25, lower main bearing 24b and upper main bearing 24a. ing. The upper main bearing 24a is configured to be lubricated by the shaft refueling upper main bearing hole 6e and the refueling main shaft groove 6k.

  A portion of the oil discharged from the oil supply pump 200 is supplied to the sub bearing 25 through a gap around the pump connection 6z.

  A rear chamber 110 which is a rear space is provided mainly below the rolling cylinder 1.

  A cylinder outer peripheral groove 2m and a frame outer peripheral groove 4m are provided on the outer peripheral portion of the compression portion. These become flow paths of the working fluid of discharge pressure. Further, an oil discharge passage 4x for draining oil from the back chamber 110 is provided on the upper surface portion to which the stationary cylinder 2 is attached.

  The suction pipe 50 is for introducing the working fluid from the outside into the compression section provided inside the casing 8. The discharge pipe 55 discharges the working fluid pressurized in the compression section to the outside. The suction pipe 50 and the discharge pipe 55 are provided on the casing upper lid 8b. Besides, a hermetic terminal 220 is provided on the casing top lid 8b. A motor wire 7b3 is connected to the hermetic terminal 220 so that power can be supplied from an external power source (not shown) to the stator winding 7b2 of the motor 7.

  The working fluid introduced from the suction pipe 50 is pressurized in the compression section and discharged from the discharge pipe 55 to the outside.

  Here, the flow of the working fluid will be described. Here, description will be made also with reference to FIG. 5 described later.

  The working fluid introduced from the suction pipe 50 is compressed in the compression section, and blows upward from the discharge hole 2d1, the bypass hole 2e, and the like. Then, the working fluid once collides with the discharge cover 230. At this time, oil contained in the working fluid adheres to the discharge cover 230 and is separated. The working fluid having a reduced amount of oil is blown out from the discharge cover port 230a and collides with the inner wall of the casing cylindrical portion 8a. This further separates the oil. Thereafter, the working fluid enters the upper casing chamber 120 and is discharged to the outside of the compressor from the discharge pipe 55 provided on the upper lid 8b of the casing. In the casing upper chamber 120, the flow velocity of the working fluid is reduced, so that the oil mist which is slightly remaining tends to settle, and the amount of oil contained in the working fluid becomes extremely small.

  On the other hand, there is no main flow of working fluid below the compression part, but working fluid of discharge pressure flows in through the cylinder outer peripheral groove 2m which is the outer peripheral groove of the compression part and the frame outer peripheral groove 4m. . As a result, the entire casing space including the lower side of the compression portion becomes the discharge pressure. That is, a high pressure chamber system is realized.

  The auxiliary bearing 25 is composed of a ball 25a and a ball holder 25b that rotatably supports the ball 25a in all directions. The lower portion of the shaft 6 is inserted into the ball 25a, and the ball 25a is mounted to the ball holder 25b, and then the ball holder 25b is fixed and arranged on the sub-frame 35 welded to the casing cylindrical portion 8a. Thus, the auxiliary bearing 25 rotatably supports the lower portion of the shaft 6.

  The RC compressor can also be installed with the central axis of the cylindrical casing directed horizontally (laterally). In this case, there is no problem even if the central axis of the cylinder is inclined. However, in this case, it is necessary to adjust the arrangement of the sub-frame peripheral holes 35a and the sub-frame central hole 35b of the sub-frame 35 which is a partition of the oil reservoir 125 so that a suitable amount of lubricating oil is retained in the oil reservoir 125 There is.

  The sub-frame 35 is provided with sub-frame peripheral holes 35 a and a sub-frame central hole 35 b. Oil is returned to the oil reservoir 125 through these holes. At the lowermost end of the shaft 6, an oil supply pump 200 is provided via a pump connection 6z to feed oil to a shaft oil supply vertical hole 6b leading to the bearings and the compression part.

  Further, oil is sealed in the casing at an appropriate stage of the RC compressor assembly, and an oil storage portion 125 for storing the oil is formed in the vicinity of the lowermost casing lower lid 8c.

  Although the cylinder groove outer peripheral wall 1 w is adopted in the present embodiment, the present invention is also realized when the cylinder groove outer peripheral wall 1 w is not adopted. In this sense, 1w is shown as a parenthesized code. Details of the cylinder groove outer peripheral wall 1 w will be described later with reference to FIG.

  Also, in the present embodiment, reference numerals in parentheses 210 and 200 'are not adopted.

  In this embodiment, the shaft 6 is directly connected to the rolling cylinder 1 of the compression unit. Thus, the rolling cylinder 1 is driven to rotate directly by the motor 7. That is, the motor 7 is a cylinder drive source.

  In FIG. 1, the shaft 6 and the rolling cylinder 1 are integrated as in a portion indicated as an M portion. In other words, the shaft 6 is fixed to the lower surface of the rolling cylinder 1. This integration may be processed from a single material, or those processed separately may be integrated by welding, diffusion bonding, or the like. In addition, when deformation occurs in integration after processing, finishing may be performed after integration. Furthermore, a joint may be provided in the M portion of FIG. 1 to transmit torque. As the joint, there may be considered an Oldham joint capable of accepting an eccentric displacement, a universal joint capable of accepting a set angular displacement, a spline joint, or the like.

  The rotating body of the rolling cylinder 1 integrated with the shaft 6 is well-balanced at the center of rotation, so that the installation of imbalance normally provided for balancing becomes unnecessary.

  Next, each element will be described individually.

  FIG. 2 shows the details of the rolling cylinder 1 of FIG.

  As shown in FIG. 2, the rolling cylinder 1 has a configuration including a cylindrical rolling cylinder 1 b and a rolling end plate 1 a. The shaft 6 is directly connected to the lower surface of the rolling cylinder 1 and fixed.

  The rolling cylinder 1b has a cylinder groove 1c. The rolling end plate 1a constitutes a bottom surface portion (a cylinder groove bottom surface portion 1c3) of the cylinder groove 1c. And the cylinder groove outer peripheral wall 1w which comprises a part of rolling cylinder 1b is provided in the outer peripheral side both ends of the cylinder groove 1c. A rolling bottom oil supply hole 1k is provided at the center of the bottom of the cylinder groove 1c. Therefore, the cylinder groove 1c is formed by the cylinder groove curved surface portion 1c1, the cylinder groove flat surface portion 1c2, and the cylinder groove bottom surface portion 1c3.

  The rolling end plate 1a of the present embodiment has a shape having a rolling mirror plate portion 1a1 projecting to the outer peripheral side of the rolling cylinder 1b from a location one step lower than the bottom surface of the cylinder groove 1c. The rolling mirror plate portion 1a1 is biased toward the lower surface of the stationary cylinder 2 to improve the sealing performance of the working chamber.

  A rolling outer periphery cut portion 1g is provided on the outer peripheral surface of the rolling cylinder 1b. A rolling outer peripheral hole 1f is provided to connect the rolling outer peripheral cut portion 1g and the side surface of the cylinder groove 1c. Furthermore, a rolling mirror plate recess 1i is provided at a portion where the rolling outer periphery cut portion 1g and the upper surface of the rolling mirror plate portion 1a1 are closest to each other. Thereby, the upper surface of the rolling mirror plate portion 1a1 is lubricated. The rolling mirror plate recess 1i is provided so as not to be in direct contact with the outer peripheral portion of the rolling mirror plate portion 1a1 (that is, not reaching the outer peripheral portion of the rolling mirror plate portion 1a1). Thereby, the discharge gas is prevented from flowing backward from the back chamber 110 which is the back space of the rolling cylinder 1 to the suction side.

  The rolling outer periphery cut part collar 1g1 is provided in the upper part of the rolling outer periphery cut part 1g. This prevents internal leakage due to communication with a suction groove (not shown) that constitutes a suction flow passage provided on the bottom surface of the cylinder hole 2b of the stationary cylinder 2 facing the rolling cylindrical upper surface 1b1 and improves compression performance. be able to.

  In the present embodiment, 1h which is a parenthesized code is not adopted.

  FIG. 3 shows the details of the orbiting piston 3 of FIG. First, the case where the reference numerals 3b1 and 3b2 with parentheses are not adopted will be described.

  As shown in FIG. 3, a piston lower surface hole 3g is provided at the center of the piston lower surface 3f. Further, a slide groove 3b is provided on the piston upper surface 3d. The depth of the slide groove 3b is a depth that communicates with the piston lower surface hole 3g. Further, on the side surface of the orbiting piston 3, two piston cut surfaces 3c parallel to each other and a piston tip surface 3e connecting them are provided. Furthermore, the slide groove 3b has a structure that reaches the piston cut surface 3c, and thereby also functions as an oil supply passage to the piston cut surface 3c.

  Next, two types of pin mechanisms 5 will be described.

  As shown in FIG. 1, the pin mechanism 5 is fixed to the bottom surface of the cylinder hole 2b and inserted into the slide groove 3b of the swing piston 3 to constitute a pin slide mechanism.

  FIG. 4A shows an example of the pin mechanism 5 configured by the slider 5 a and the fixing pin 5 s.

  In the figure, the pin mechanism 5 is shown in a state of being disassembled into the slider 5a and the fixing pin 5s.

  The slider 5 a has a substantially rectangular parallelepiped shape, and has a slider even surface 5 a 1 that slides on the slide groove 3 b (FIG. 3) of the orbiting piston 3. In other words, the slider 5a has a slider even surface 5a1 slidably in contact with the slide groove 3b (FIG. 3). The slider 5a also has a slider shaft hole 5a10 and a slider groove 5a2. The slider groove 5a2 is provided on the slider even surface 5a1 for lubrication.

  On the other hand, the fixing pin 5s has a substantially cylindrical shape, and a fixing pin flange 5s3 is provided at the lower end thereof. Further, the fixing pin 5s is provided with a fixing pin oiling vertical hole 5s1 and a fixing pin oiling horizontal hole 5s2. The fixing pin oil supply vertical hole 5s1 has an opening on the lower surface of the fixing pin flange 5s3. The fixing pin oil supply horizontal hole 5s2 has an opening at the side surface of the fixing pin 5s, and is connected to the fixing pin oil supply vertical hole 5s1 inside the fixing pin 5s.

  The fixing pin 5s is inserted into and fixed to the slider shaft hole 5a10 of the slider 5a. The slider 5a is installed in a state in which the central axis of the pin mechanism 5 is the rotation axis (a state in which the slider 5a can be rotated about the fixing pin 5s). The fixing pin flange 5s3 axially supports the slider 5a. The fixing pin oil supply vertical hole 5s1 and the fixing pin oil supply horizontal hole 5s2 form an oil supply path to the sliding portion between the slider 5a and the fixing pin 5s.

  FIG. 4B shows another example, a pin mechanism 5 configured of a slider 5a and a pin bearing 5c.

  In the figure, the pin mechanism 5 is shown in a state of being disassembled into the slider 5a and the pin bearing 5c.

  The slider 5a has a shape in which a substantially rectangular parallelepiped portion and a substantially cylindrical slider rotation pin 5a3 are combined, and has a slider coupled surface 5a1 sliding on the slide groove 3b (FIG. 3) of the orbiting piston 3. Further, the slider 5a has a slider groove 5a2. The slider groove 5a2 is provided on the slider even surface 5a1 for lubrication. The slider rotation pin 5a3 is a shaft portion of the slider 5a. A slider oil supply vertical hole 5a4 and a slider oil supply horizontal hole 5a5 are provided inside the slider 5a. The slider oil supply vertical hole 5a4 has an opening on the lower surface of the substantially rectangular parallelepiped portion of the slider 5a. The slider oil supply horizontal hole 5a5 has an opening at the side surface portion of the slider rotation pin 5a3, and is connected to the slider oil supply vertical hole 5a4 inside the slider 5a.

  On the other hand, the pin bearing 5c has an annular shape and is sandwiched between the slider 5a and the stationary cylinder 2 (FIG. 1) into which the slider 5a is inserted.

  The slider oil supply vertical hole 5a4 and the slider oil supply horizontal hole 5a5 form an oil supply path to the sliding portion between the slider 5a and the pin bearing 5c, and lubricate the bearing portion.

  The pin bearing 5c may be a bearing bush constituting a slide bearing, or may be a rolling bearing such as a ball bearing or a roller bearing. The configuration of FIG. 4B is suitable for a large-capacity compressor because the diameter and length of the shaft portion can be set larger compared to the configuration of FIG. 4A.

  Further, as a configuration common to FIGS. 4A and 4B, there is a slider even surface 5a1 which slides with the slide groove 3b to form a pair. Since the slider even surface 5a1 is a portion receiving a large force from the working fluid as described later, extremely high load resistance is required. In the present embodiment, the side surfaces of the slider even surface 5a1 and the slide groove 3b are both flat, and thus form a surface even. As a result, load bearing performance is improved, and the reliability of the compressor can be improved. Further, in the present embodiment, since the slider groove 5a2 is provided in the slider even surface 5a1, oil enters the surface even and lubricates. For this reason, load bearing performance is further improved.

  Next, the shaft 6 will be described with reference to FIG.

  In the drawing, a shaft oil supply vertical hole 6b penetrates the shaft 6 along its central axis. The shaft 6 is provided with a shaft refueling sub-horizontal hole 6g, which is a refueling path to the sub bearing 25, and a shaft refueling lower main bearing hole 6f, which is an refueling path to the main bearing 24, and a shaft refueling upper main bearing hole 6e. It is done. Further, on the side surface portion of the shaft 6, there is provided a lubrication main shaft groove 6k which extends from the shaft lubrication upper main bearing hole 6e to the rear chamber 110.

  By the way, as shown in FIG. 2, the upper opening of the shaft oil supply vertical hole 6b is connected with the rolling bottom oil supply hole 1k so as not to generate a leak flow path. Further, at the lower end portion of the shaft 6, a pump connection portion 6 z for inserting into the fuel supply pump 200 protrudes. And the shaft oil supply vertical hole 6b is opened in the center.

  Next, the fuel supply pump 200 will be described with reference to FIG.

  FIG. 6 is an exploded perspective view showing the fuel supply pump 200. As shown in FIG. In FIG. 6, reference numerals 204 'and 200' in parentheses are not employed.

  The feed pump 200 uses the principle of a rolling cylinder type positive displacement fluid machine, similar to the above-described compression unit. Since the oil supply pump 200 uses oil with a low vapor pressure as the working fluid, it is configured to function as a pump that does not cause a compression operation. That is, the type is not a type in which the oil supply rotation piston 203 is driven to rotate, but is a type in which the oil supply rolling cylinder 201 is rotationally driven coaxially with the shaft 6. As a result, the eccentric shaft for the oil supply pump necessary to drive the oil supply rotation piston 203 becomes unnecessary, and the structure is simplified, and the manufacturing cost is reduced.

  First, the configuration of the fuel supply pump 200 will be described with reference to FIG.

  The feed pump 200 includes a feed stationary cylinder 202, a feed rolling cylinder 201, a feed orbiting piston 203, and a feed lid 204.

  The oil supply stationary cylinder 202 has an oil supply shaft through hole 202a and an oil supply cylinder hole 202b.

  The oil supply rolling cylinder 201 has an oil supply cylinder groove 201c and an oil supply shaft connection hole 201d.

  The refueling pivot piston 203 has a refueling pin groove 203b and a refueling back hole 203g.

  The fueling lid 204 is provided with a fueling pin 205 at a position off the center thereof. In other words, the filler pin 205 is provided at an eccentric position different from the center of the filler lid 204. In addition, the fueling lid 204 has a fueling discharge groove 204d, a fueling communication groove 204e, a fueling suction groove 204s, and a fueling suction hole 204h. The fuel communication groove 204 e is connected to the fuel discharge groove 204 d, and has a shape that surrounds the fuel pin 205 and extends to the central portion of the fuel lid 204.

  When assembling the oil supply pump 200, the oil supply rolling cylinder 201 is inserted into the oil supply cylinder hole 202b of the oil supply stationary cylinder 202, the pump connecting part 6z is passed through the oil supply shaft through hole 202a, and then the pump connecting part 6z is supplied It inserts in connection hole 201d. Then, after the oil supply rotation piston 203 is clearance fitted to the oil supply cylinder groove 201c, the oil supply lid 204 provided with the oil supply pin 205 eccentrically is provided from the lower side. Here, the fueling pin 205 is inserted into the fueling pin groove 203 b of the fueling rotation piston 203. Then, finally, it is fixed to the sub-frame 35 (FIG. 1) with three fueling bolts 209.

  In the present embodiment, although the assembly of the oil supply pump 200 and the attachment to the sub frame 35 are simultaneously performed using the oil supply bolt 209, first, after the assembly of the oil supply pump 200 is performed, It may be a two-step process of mounting. As a result, the assembly accuracy of the assembly is improved, and the high performance of the fuel pump 200 can be realized.

  Next, the operation of the fuel supply pump 200 will be described with reference to FIG.

  FIG. 15 is a top view of a cross section of the height at which the fueling pin 205 is inserted into the fueling pin groove 203b when the fueling pump 200 of FIG. 6 is assembled, and the arrow indicates the fueling rolling cylinder 201 (shaft 6) rotation direction.

  FIG. 15 shows the timing at which the working chamber on the left side of the refueling swirl piston 203 completes the discharge stroke and changes from the refueling discharge chamber 212 to the refueling suction chamber 211. At this time, the working chamber on the right side ends the suction stroke, and changes from the refueling suction chamber 211 to the refueling discharge chamber 212.

  By forming the oil supply and discharge groove 204d into a crescent shape expanded right below the right working chamber, the rolling cylinder positive displacement compressor does not have a generated compression stroke. When the shaft 6 rotates in the direction of the arrow in FIG. 15, the oil supply rolling cylinder 201 connected to the pump connecting portion 6z (FIG. 6) rotates, and the oil supply swirl piston 203 in the oil supply cylinder groove 201c (FIG. 6) also rotates. .

  However, as a result of the position and attitude of the oil supply pin groove 203b being restricted by the oil supply pin 205, the oil supply rotation piston 203 rotates at the middle point of the line segment connecting the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201. Then, a pivoting motion is performed with a distance between the center of the fueling pin 205 and the center of the fueling rolling cylinder 201 as a pivoting diameter. Accordingly, the refueling swirl piston 203 relatively reciprocates in the refueling cylinder groove 201 c with a stroke twice the distance between the center of the refueling pin 205 and the center of the refueling rolling cylinder 201.

  As a result, the oil in the oil storage portion 125 is sucked up from the refueling suction hole 204h and is sent out to the refueling communication groove 204e. Then, the oil is finally fed to the shaft oil supply vertical hole 6b (FIG. 6) via the oil supply pin groove 203b and the oil supply back surface hole 203g (FIG. 6).

  Next, features and effects of the feed pump 200 will be described.

  In the free piston system in which the oil supply rolling cylinder 201 is rotationally driven and the oil supply rotation piston 203 is restricted by the movement of the oil supply pin 205, assembly is extremely easy. In the rolling cylinder type, which is another type of rolling cylinder type, the center axis of the fueling pin and the center axis of the oiling rolling cylinder are on the swinging trajectory of the oiling pivot piston, and they further oppose 180 degrees. If you do not place it, the pump will not operate and will lock.

  However, in this method, in consideration of the relative reciprocating motion of the orbiting piston in the oil supply cylinder groove, assembly is possible only by controlling the center axis of the oil supply pin within a certain value from the center axis of the oil supply rolling cylinder. . This has the effect that the manufacturing cost can be reduced.

  In addition, compared with a gear pump such as a trochoid oil pump, the shape of the component is simple, so high accuracy can be realized at low cost, and the compressor efficiency is improved by the improvement of the oil pump performance, and the manufacturing cost is reduced. Has the effect of realizing Moreover, since the peak of the oil supply discharge amount appears twice during one rotation of the shaft 6 (FIG. 6), the reliability of the bearing can be improved by matching the oil discharge amount with the peak of the load at the bearing portion. It has the effect of

  Next, the flow of the working fluid (refrigerant etc.) will be described.

  The working fluid enters the compression section from the suction system outside the RC compressor through the suction pipe 50 (FIG. 1) and is pressurized by the same compression operation as in Patent Document 1. The boosted working fluid spouts out of the discharge passage (symbol 2d in FIG. 5) to the upper part of the stationary cylinder 2. In the over compression condition where the operating pressure ratio is lower than the pressure ratio corresponding to the specific volume ratio of the RC compressor, the working fluid also ejects from the bypass hole 2e via the bypass valve 22 (FIG. 1).

  Then, as shown in FIG. 1, it collides with the discharge cover plate 230b of the discharge cover 230 fixedly disposed at the upper part of the stationary cylinder 2, and after separating much of the oil contained in the working fluid, it deviates from the radial direction As a swirl flow from the discharge cover port 230a provided at an angle substantially along the inner wall of the discharge cover chamber 130, it spouts into the swirl chamber 140. There, oil remaining in the working fluid adheres to the inner wall of the casing cylindrical portion 8a by centrifugal force and is separated. And finally, it enters the casing upper chamber 120 while the flow direction is changed from the outer peripheral clearance of the discharge cover plate 230b at the lower end face of the casing upper lid 8b, and the oil that could not be separated is separated by sedimentation. The pipe 55 exits the discharge system outside the RC compressor.

  Thereby, there is no main flow of working fluid flowing into the lower part of the compression part, but the working fluid of discharge pressure flows in through the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m, so the entire casing space including the lower part of the compression part is discharged It becomes pressure.

  As described in the following oil flow description, in particular, since the back chamber 110 on the back of the rolling cylinder 1 also has a discharge pressure, the rolling cylinder 1 is biased to the stationary cylinder 2 while sandwiching the orbiting piston 3 to operate The axial clearance that forms the seal of the chamber is reduced. As this axial gap, a gap between the piston upper surface 3d and the bottom of the cylinder hole 2b, a gap between the piston lower surface 3f and the bottom of the cylinder groove 1c, a gap between the rolling cylinder upper surface 1b1 and the bottom of the cylinder hole 2b, and There is a gap between the upper surface of the rolling mirror plate portion 1a1 and the lower surface of the stationary cylinder 2 (around the cylinder hole 2b). As a result, the sealability is improved, and the compressor efficiency is improved.

  Furthermore, when a conformable coating is provided on these surfaces, the gap is further narrowed, the sealability is further improved, and the compressor efficiency is further improved. As such a film, for example, when the material is cast iron, there is a manganese phosphate compound. In particular, in order to reduce the clearance between the rolling cylinder upper surface 1b1 and the bottom of the cylinder hole 2b and the clearance between the upper surface of the rolling mirror plate portion 1a1 and the lower surface of the stationary cylinder 2 (around the cylinder hole 2b) Leakage of the working fluid at the discharge pressure to the compression chamber 100 and the suction chamber 95 is significantly reduced, and there is an effect of improving the volumetric efficiency and the compressor efficiency.

  Next, the flow of oil will be described.

  As shown in FIG. 1, the oil of the oil storage portion 125 is fed to the shaft oil supply vertical hole 6 b via the pump connection portion 6 z by the operation of the oil supply pump 200 described above. And as above-mentioned, it supplies to each bearing part (sub bearing 25, the lower main bearing 24b, the upper main bearing 24a) through an oil supply horizontal hole. Among these, the oil supplied to the upper main bearing 24a and the lower main bearing 24b enters the back chamber 110 via the oil supply spindle groove 6k. The oil that has entered the back chamber 110 is then discharged to the top surface of the stator 7b through the oil discharge passage 4x, through the frame outer peripheral groove 4m. As a result, the back pressure that is the pressure of the back chamber 110 becomes the discharge pressure.

  As a result, the movable portion constituted by the rolling cylinder 1 and the orbiting piston 3 is always biased to the stationary cylinder 2. As a result, the axial gap between the piston upper surface 3d and the piston lower surface 3f of the orbiting piston 3 and the upper surface of the rolling cylinder 1b of the rolling cylinder 1 and the rolling mirror plate portion 1a1 is reduced, sealing performance is improved, and compressor efficiency is improved. . Here, since the oil discharge passage 4x is at the same height as the sliding portion of the lower surface of the stationary cylinder 2 and the upper surface of the rolling mirror plate portion 1a1, the oil level of the back chamber 110 rises to the sliding portion, and the lubrication and sealability are achieved. There is an effect of realizing improvement of

  Further, the oil in the shaft oil supply vertical hole 6b enters the piston lower surface hole 3g of the orbiting piston 3 via the rolling bottom oil supply hole 1k. And it enters into the slide groove 3b from there. The oil contained in the slide groove 3b lubricates the sliding portion of the pin mechanism 5 and the slide groove 3b, and enters the sliding gap between the orbiting piston 3 and the stationary cylinder 2 and the rolling cylinder 1 to lubricate and seal. . The oil in each gap enters the working chamber again and mixes with the working fluid. Then, the working fluid is mixed with the working fluid and discharged from the discharge passage 2 d to the discharge cover chamber 130.

  Furthermore, part of the oil flows into the rolling peripheral cut portion 1g through the rolling peripheral hole 1f. The oil contained therein lubricates the gap between the outer circumference of the rolling cylinder 1b and the inner circumference of the cylinder hole 2b. Further, it enters a rolling mirror plate recess 1i provided below the rolling outer periphery cut portion 1g, and lubricates between the upper surface of the rolling mirror plate portion 1a1 and the lower surface of the stationary cylinder 2.

  On the other hand, the oil that has flowed into the working chamber via various seal gaps mixes with the working fluid in the working chamber, and when the working fluid enters the leak flow path during suction, compression or discharge stroke, the inside of the leak flow path Form an oil film on the inside to suppress internal leakage. Furthermore, since the majority of the leak channels are relative motion points between the compression elements, the inflowing oil reduces friction and improves lubricity. Thus, there is an effect of improving the compressor efficiency. The oil mixed with the working fluid in this manner, together with the internal circulation in the working chamber, finally jets out together with the working fluid to the discharge cover chamber 130 as described in the description of the flow of the working fluid, and operates stepwise. Separate from the fluid. The oil separated in this manner is discharged to the upper surface of the stator 7b in the lower space of the compression portion through the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m on the outer periphery of the compression portion.

  As a result, all the oil that has risen to the compression section through the shaft oil supply vertical hole 6b gathers on the upper surface of the stator 7b. Thereafter, the space under the motor 7 is reached through a hole through which the outer peripheral stator cut surface 7b1 and the stator winding 7b2 pass. Thereafter, a small amount passes through the sub-frame central hole 35 b and feeds the inner and outer peripheries of the balls 25 a of the sub bearing 25, and then returns to the oil reservoir 125 through the sub-frame peripheral hole 35 a.

  Next, the compression operation in the compression unit will be described using FIG. 5, and the operation and effects of the invention will be described.

  FIG. 5 is a flowchart showing the compression stroke of the RC compressor according to the first embodiment.

  In one compression stroke shown in the figure, the shaft 6 (rolling cylinder 1) rotates 180 degrees. That is, when the shaft makes one rotation, two compression strokes are performed.

  When the shaft 6 rotates from the upper left shaft rotation angle 0 degree in FIG. 5, the suction groove 2s2 is provided with the working chambers on the upper side of each stage at the bottom of the cylinder hole 2 b (FIG. 1) of the stationary cylinder 2. Because it takes on the suction passage 2s of the suction hole 2s1, it becomes the suction chamber 95. On the other hand, the working chamber on the opposite side becomes the compression chamber 100 or the discharge chamber 105. For this reason, a force is applied to the orbiting piston 3 from the working fluid by the pressure difference between both working chambers.

  In FIG. 5, this force vector is indicated by the open arrow drawn from the compression chamber 100 at each stage to the orbiting piston 3. Further, a force vector exerted by the slider 5a of the pin mechanism 5, which is the support portion, on the swing piston 3 against this force is indicated by a black arrow described near the rotation center of each step.

  As apparent from FIG. 5, the lines of action of the two forces are always shifted except for the zero shaft rotation angle. Therefore, the two forces become a couple and the swing piston 3 tries to rotate. Since there is always a gap in an actual element part, a minute rotation occurs in practice. It can be seen from FIG. 5 that the direction of rotation is always counterclockwise.

  Accordingly, the orbiting piston 3 contacts the rolling cylinder 1 at a black circle (a boundary corner between the piston cut surface 3c and the piston tip surface 3e in FIG. 3). And since the contact point is always the same place as shown in FIG. 5, it can be seen that there is no time when the contact disappears. In addition, since the force is completely balanced only when the shaft rotation angle is 0 degree, the contact is not necessary, but in that case, the inertia continues to keep rotating while keeping the contact.

  Although this contact causes the rolling cylinder 1 to receive a counterclockwise turning torque, the motor 7 which is a cylinder drive source of the rolling cylinder 1 applies a torque against it, so that the rolling cylinder 1 does not turn counterclockwise. The compression operation continues.

  As a result, the rolling cylinder 1 and the orbiting piston 3 always contact each other, so that no rotational play occurs between them. As a result, the swing piston 3 does not collide with the side surface of the cylinder groove 1 c of the rolling cylinder 1, so that vibration and noise can be reduced. In addition, since the impact force no longer acts on the side surface portion of the cylinder groove 1c (FIG. 2) and the boundary corner portion between the piston cut surface 3c and the piston tip surface 3e of the swing piston 3 which is the other, sliding loss And wear are reduced, and compressor performance and reliability are improved. Furthermore, since the force applied to the pin mechanism 5 which is the support portion of the orbiting piston 3 is also no impact force due to the collision, the reliability of the pin mechanism 5 is improved. Furthermore, although the side surface portion of the cylinder groove 1c and the piston cut surface 3c constitute a seal portion, a stable oil film is formed and high sealability can be realized since the contact condition on both surfaces is stable, and leakage There is also an effect that the compressor performance is improved by

  Further, as another modification of the present embodiment, a slide groove wall shown by reference numeral 3b1 in FIG. 3 may be adopted. This connects the both ends of the slide groove 3b, and has an effect of enhancing the rigidity of the swing piston 3. In particular, in a rolling cylinder positive displacement compressor of a type in which only the rolling cylinder 1 is driven as in the present embodiment, the pivot piston 3 to which a compressive load of the working fluid is applied is supported by the pin mechanism 5. For this reason, a large load is applied to the side surface of the slide groove 3b. Therefore, it is necessary to make the slide groove 3b deeper in order to reduce the surface pressure, but by providing the slide groove wall 3b1, the surface pressure received from the pin mechanism 5 can be reduced without reducing the rigidity of the orbiting piston 3 It will be possible. In this modification, the slide groove wall 3b1 is provided with a hole for supplying oil to the piston cut surface 3c and the rolling outer peripheral hole 1f, so as not to inhibit the flow of oil.

  Furthermore, as another modification, slide groove digging indicated by reference numeral 3b2 in FIG. 3 may be provided. As a result, when the slider 5a relatively moves in the slide groove 3b, the effect of reducing the resistance of the oil in the slide groove 3b and the effect of adjusting the amount of oil supplied to the rolling outer peripheral hole 1f to an appropriate amount can be obtained.

  The RC compressor according to the second embodiment will be described with reference to FIGS. 7 to 13.

  FIG. 7 is a longitudinal sectional view showing the RC compressor of the present embodiment. The parenthesized code 1w is adopted, and 210 and 200 'are not adopted.

  Hereinafter, the description of the same configuration as that of the first embodiment will be omitted.

  In this embodiment, together with a cylinder drive source for driving the rolling cylinder 1 to rotate, there is provided a piston rotation source for driving the orbiting piston 3 by means of a crank shaft. Furthermore, the slider is provided in the pin mechanism which is a support part of a piston.

  The shape of the shaft 6 in the compression section is different. Along with this, the main balance 80 is installed above the rotor 7a, and the counterbalance 82 is installed below the rotor 7a. Besides, the shapes of the rolling cylinder 1, the swing piston 3 and the pin mechanism 5 are partially different from those of the first embodiment.

  FIG. 8 is an enlarged view of a portion L in FIG.

  FIG. 9 is a top perspective view of the rolling cylinder 1 of FIG. FIG. 10 is a bottom perspective view of the rolling cylinder 1 of FIG. The parenthesized code 1h is not adopted.

  As shown in FIG. 8, the shaft 6 has a large diameter shaft collar 6c at its upper part. The upper surface of the shaft collar 6c is called a cylinder contact surface 6m. And, on the cylinder contact surface 6m, an eccentric shaft 6a having an eccentricity of half the distance between the central axis of the pin, which is the central axis of the pin mechanism 5, and the cylinder axis is installed. That is, in the present embodiment, the eccentric shaft 6a is a crank type shaft which is made to project.

  Further, the upper end portion of the eccentric shaft 6a is provided with the opening of the shaft oil supply vertical hole 6b, and the outer periphery of the eccentric shaft 6a is provided with a shaft oil eccentric groove 6h.

  The rolling cylinder 1 also has an eccentric shaft insertion hole 1d shown in FIG. 9 at the center of the lower surface of the cylinder groove 1c. The eccentric shaft 6a is adapted to be inserted into the eccentric shaft insertion hole 1d. A shaft collar contact surface 1e shown in FIG. 10 is provided on the back peripheral edge of the eccentric shaft insertion hole 1d.

  The orbiting piston 3 rotates on the central axis of the eccentric shaft 6a as a rotation axis, and revolves on the central axis of the shaft 6 (drive transmission portion) as a rotation axis.

  FIG. 11 is a perspective view showing the orbiting piston of the RC compressor of the present embodiment.

  As shown in this figure, the orbiting piston 3 has an orbiting bearing hole 3a, and the orbiting bearing 23 is fixedly disposed there.

  FIG. 12 is a perspective view showing a pin mechanism of the RC compressor of the present embodiment.

  As shown in this figure, the pin mechanism 5 is configured to use the fixing pin 5s as in FIG. 4A of the first embodiment, but the slider pair surface 5a1 is set to have a small area because the load is small. .

  Next, the configuration of the compression unit using an element having a change from the first embodiment as described above will be described.

  In FIG. 8, the eccentric shaft 6 a is inserted into the eccentric shaft insertion hole 1 d of the rolling cylinder 1, and is inserted into the pivot bearing 23 of the pivot piston 3.

  In this embodiment having this configuration, when the shaft 6 is rotated by the motor 7, the orbiting piston 3 pivots and a compression operation occurs. In this case, the motor 7 is a piston rotation source using a crank shaft 6. The shaft 6 is pushed up by the axial thrust generated by the motor 7 as in the first embodiment. As a result, as clearly shown in FIG. 8, the cylinder contact surface 6 m which is the upper surface of the shaft collar 6 c is biased to the shaft collar contact surface 1 e on the back surface of the rolling cylinder 1.

  FIG. 13 is a schematic view of the contact portion as viewed from the lower side of the shaft 6.

  In this figure, since the shaft 6 rotates in the same direction as the rolling cylinder 1, the rolling cylinder 1 is rotationally driven without the pivot piston 3. That is, the motor 7 is also a cylinder drive source. That is, in the RC compressor of the present embodiment, the rotation drive of the rolling cylinder 1 and the swing drive of the swing piston 3 are simultaneously performed by one motor 7.

  Next, the compression operation will be described, and the effects of the invention will be described.

  Although how the force is applied is different, the transition of the working chamber during the operation of the RC compressor is the same as that of the first embodiment shown in FIG.

  As shown in FIG. 5, the rotational speed of the rolling cylinder 1 is half of the pivoting speed of the pivoting piston 3. The rotational speed of the shaft 6 in the present embodiment is in agreement with the rotational speed of the orbiting piston 3 so that a deviation from the rotational speed of the rolling cylinder 1 occurs. However, since the rotational torque transmission from the shaft 6 to the rolling cylinder 1 is performed by urging the flat plates, it is possible even if there is a difference between the rotational speed and the rotational center. Furthermore, the torque required for the rolling cylinder 1 is extremely small because there is no torque due to the pressure of the working fluid, and the torque that can be transmitted by biasing between the flat plates is sufficient. For this reason, the rotation of the rolling cylinder 1 accelerates the movement of the orbiting piston 3 and the points of the black circles in FIG. 5 always contact to assist the orbiting movement of the orbiting piston 3 though slightly. And since the contact point is always the same place as is clear from FIG. 5, it can be seen that there is no time when the contact disappears. In the present embodiment, unlike the first embodiment, even when the shaft rotation angle is 0 degree, the contact continues at the same place.

  As a result, the rolling cylinder 1 and the orbiting piston 3 are in constant contact with each other, so that rotational rattling does not occur between them, and the same effect as in the first embodiment is obtained.

  As an effect of only this embodiment, since the main support portion of the swing piston 3 is the eccentric shaft 6a, the force applied to the pin mechanism 5 which is another support portion becomes extremely small, and the reliability of the pin mechanism 5 is improved. It has the effect of greatly improving. Therefore, as shown in FIG. 12, the slider even surface 5a1 can be reduced in size to increase the size of the bearing portion, and the reliability can be improved.

  In order to enhance the torque transmission efficiency between the cylinder contact surface 6m and the shaft collar contact surface 1e shown in FIG. 8, the surface roughness may be increased. For example, when the material of the rolling cylinder 1 is cast iron, it may be considered to make the shaft collar contact surface 1e a surface where a cast surface is slightly left. In addition, it may be a pear ground by electric discharge machining or the like. Moreover, you may perform groove processing of a record groove shape with a lathe.

  By the way, the rolling cylinder 1 of Examples 1 and 2 has the cylinder groove outer peripheral wall 1 w. In this type, the sealability between the working chambers is high, but the force received from the working fluid (a force opposite to the direction indicated by the black arrow in FIG. 5) presses the outer peripheral surface of rolling cylinder 1b against the inner peripheral surface of cylinder hole 2b. And the sliding loss increases.

  Therefore, as shown in FIG. 2, FIG. 9, and FIG. 10, it is conceivable to open the rolling balance hole 1h substantially at the center of the cylinder groove outer peripheral wall 1w. The rolling balance hole 1h has a cross-sectional area equivalent to the longitudinal cross section (rectangular gap cross section) of the outer peripheral surface of the rolling cylinder 1b and the inner peripheral surface of the cylinder hole 2b. As a result, the pressure difference on both sides of the cylinder groove outer peripheral wall 1 w is reduced, and the force by which the outer peripheral surface of the rolling cylinder 1 b is pressed against the inner peripheral surface of the cylinder hole 2 b is reduced. As a result, the sliding loss can be reduced, and the compressor efficiency can be improved. Here, at the lower part of the outer peripheral surface of the rolling cylinder 1b, as described above, the upper surface of the rolling mirror plate portion 1a1 seals the rear chamber 110 of the discharge pressure.

  The RC compressor according to the third embodiment will be described with reference to FIG.

  FIG. 14 is a perspective view of a rolling cylinder of the RC compressor according to the third embodiment.

  Hereinafter, an example will be described in which the rolling cylinder 1 'shown in the figure has any one of the holes 1k or 1d in parentheses.

  The case of having the rolling bottom oiling hole 1k is similar to that of the first embodiment.

  On the other hand, the case of having the eccentric shaft insertion hole 1d is the same as that of the second embodiment.

  Descriptions other than the points different from Embodiment 1 or 2 will be omitted.

  In this embodiment, in either case, both ends of the cylinder groove 1c are removed, so that the processing is facilitated and the manufacturing cost is reduced. Further, when the rolling outer periphery cut groove portion 1g2 is provided at the rear in the rotational direction of the rolling outer periphery cut portion 1g, the oil flowing in from the rolling outer periphery hole 1f is held therein, and between the operating chambers formed on both sides of the orbiting piston 3 There is an effect of suppressing the leakage and improving the compressor efficiency.

  The feed pump of the RC compressor according to the fourth embodiment will be described with reference to FIG.

  In FIG. 16, the fuel supply lid 204 shown by F in FIG. 6 is changed to a variable fuel supply lid 204 'to form a variable displacement fuel supply pump 200'. Other than the above, the second embodiment is the same as the first to third embodiments, so the description of the overlapping portion is omitted, and the different portion is mainly described.

  In the fuel supply pump 200 of FIG. 6, the fuel supply pin 205 is fixed to the fuel supply lid 204.

  On the other hand, in the present embodiment, a variable oil supply lid 204 'shown in FIG. 16 is used instead of the oil supply lid 204 of FIG. 6 to incorporate a mechanism capable of moving the oil supply pin 205. Is realized.

  In the case of the rolling cylinder type lubrication pump, as shown in FIG. 6, as the lubrication pin groove 203b is restricted in position and posture by the lubrication pin 205, the center of the lubrication pin 205 and the lubrication rolling cylinder A pivoting motion is performed with the center point of the center of 201 as the pivot center and the distance between the center of the fueling pin 205 and the center of the oil feeding rolling cylinder 201 as the pivot diameter. Accordingly, the refueling swirl piston 203 reciprocates relatively within the refueling cylinder groove 201 c with a stroke twice the distance between the center of the refueling pin 205 and the center of the refueling rolling cylinder 201. From this, when the center of the oil supply pin 205 is shifted with respect to the shaft rotation axis which is the central axis of the oil supply rolling cylinder 201, the capacity of the oil supply pump can be changed.

  In this embodiment, the displacement of the oil supply pump is changed by the movement of the oil supply pin 205 as follows.

  In the present embodiment, as shown in FIG. 16, the variable fueling lid 204 'is configured of a fueling channel plate 204a, a fueling pin base 204b, and a fueling pin base retainer 204c. A refueling suction groove 204s, a refueling discharge groove 204d, and a screw hole are opened in the refueling passage plate 204a. A filler pin 205 is installed in the filler pin base 204b, and a filler pin drive screw hole 204b1 is provided on the lateral tip surface. Further, an oiling pin slide hole 204c1, an oiling suction hole 204h, and a screw hole in which the oiling pin base 204b slides are opened in the oiling pin base holder 204c. The oil supply passage plate 204a, the oil supply pin base 204b and the oil supply pin base holder 204c are overlapped, and the oil supply pin slide screw 210a rotationally driven by the oil supply pin slide motor 210 is screwed into the oil supply pin drive screw hole 204b1. The variable fuel supply lid 204 'produced in this manner is used as a variable displacement fuel supply pump 200' in the same manner as in FIG.

  When operating the variable displacement oil supply pump 200 ′, the oil supply pin slide motor 210 is driven by an oil supply pin slide power supply line (not shown) for supplying power from the outside, and the oil supply pin base 204 b is slid. As a result, it is possible to move the fueling pin 205 and freely change the capacity of the fueling pump. As a result, it is possible to optimize the amount of refueling under various operating conditions, such as solving the drawback of the refueling pump in which refueling is excessive when the rotational speed is high, by reducing the capacity of the refueling pump. . This has the effect of improving the compressor efficiency under various operating conditions.

  The effects of the present invention will be summarized and described below.

  According to the present invention, among the movable compression elements that cooperate to form the compression chamber, the pivot piston exerts a large force from the working fluid by applying a rotational drive torque to the rolling cylinder where the torque does not work from the working fluid. The range of the play with the rolling cylinder is shifted to the smallest turning angle. Finally, the rolling cylinder and the sliding portion collide with each other. However, since a large force is acting on the orbiting piston in the direction to reduce the orbiting angle from the working fluid, the orbiting piston does not advance the orbiting angle even by this collision, and always contacts the rolling cylinder. Counter the force from the working fluid and continue the pivoting motion.

  As a result, a collision at the sliding portion is avoided, vibration noise and wear are suppressed, and the reliability is improved. Furthermore, the impact load on the sliding portion is suppressed, the leakage loss can be realized by the reduction of the sliding loss due to the reduction of the sliding load, and the improvement of the oil film formation by the stabilization of the sealing gap of the sliding portion, and the compressor performance is improved. Can be

  1: Rolling cylinder, 1a: rolling end plate, 1a1: rolling mirror plate portion, 1b: rolling cylinder, 1b1: rolling cylinder upper surface, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 1e: shaft collar contact surface, 1f: rolling Outer peripheral hole, 1g: rolling outer peripheral cut portion, 1g1: rolling outer peripheral cut portion collar, 1g2: rolling outer peripheral cut groove portion, 1h: rolling balance hole, 1i: rolling mirror plate recess, 1k: rolling bottom oiling hole, 1w: cylinder groove outer peripheral wall 2, 2: stationary cylinder, 2b: cylinder hole, 2d: discharge passage, 2e: bypass hole, 2m: cylinder outer peripheral groove, 2s: suction passage, 2s 1: suction hole, 2s 2: suction groove, 3: swirl piston, 3a: swirl Bearing hole, 3b: slide groove, 3b1: slide groove wall, 3b2: slide groove digging, 3c: Stone cut surface, 3d: piston upper surface, 3e: piston tip surface, 3f: piston lower surface, 3g: piston lower surface hole, 4: frame, 4m: frame outer peripheral groove, 4x: oil discharge path, 5: pin mechanism, 5a: slider , 5a1: slider even surface, 5a2: slider groove, 5a3: slider rotating pin, 5a4: slider oil vertical hole, 5a5: slider oil horizontal hole, 5a10: slider shaft hole, 5s: fixing pin, 5s1: fixing pin oil vertical hole, 5s2: Fixing pin oiling horizontal hole, 5s3: Fixing pin flange, 5c: pin bearing, 6: shaft, 6a: eccentric shaft, 6b: shaft oiling vertical hole, 6c: shaft collar, 6e: shaft oiling upper main bearing hole, 6f: shaft oiling Lower main bearing hole, 6g: shaft refueling sub lateral hole, 6h: shaft refueling eccentric groove, 6k: refueling spindle groove, 6m: cylinder contact Surface 6z: pump connection portion 7: motor 7a: rotor 7b: stator 7b1: stator cut surface 7b 2: stator winding 7b 3: motor wire 8a: casing cylindrical portion 8b: casing upper lid 8c : Casing lower lid, 22: Bypass valve, 23: Swiveling bearing, 24: Main bearing, 24a: Upper main bearing, 24b: Lower main bearing, 25: Secondary bearing, 25a: Ball, 25b: Ball holder, 35: Subframe , 35a: subframe peripheral hole, 35b: subframe central hole, 50: suction pipe, 55: discharge pipe, 80: main balance, 82: counter balance, 90: cylinder bolt, 95: suction chamber, 100: compression chamber, 105: Discharge chamber, 110: Back chamber, 120: Casing upper chamber, 125: Oil reservoir, 130: Discharge cover chamber, 140: Swirl chamber, 200: Refueling port Pump 200: Variable displacement oil pump 201: Refueling rolling cylinder 201c: Refueling cylinder groove 201d: Refueling shaft connection hole 202: Refueling stationary cylinder 202a: Refueling shaft through hole 202b: Refueling cylinder hole 203: Refueling turning piston, 203b: refueling pin groove, 203g: refueling back hole, 204: refueling lid, 204 ': variable refueling lid, 204a: refueling passage plate, 204b: refueling pin base, 204b1: refueling pin drive screw hole, 204c: Refueling pin base holder, 204c1: Refueling pin slide hole, 204d: Refueling discharge groove, 204e: Refueling communication groove, 204h: Refueling suction hole, 204s: Refueling suction groove, 205: Refueling pin, 209: Refueling bolt, 210: Refueling pin Motor for slide, 210a: Oil supply pin slide screw, 211: Oil supply and suction Chamber, 212: oil supply discharge chamber, 220: hermetic terminal, 230: discharge cover, 230a: discharge cover openings, 230b: discharge cover plate.

Claims (7)

A cylindrical rolling cylinder having a cylinder groove;
A swing piston having a slide groove;
Stationary cylinder,
Pin mechanism,
Driving source,
A drive transmission unit connecting the rolling cylinder and the drive source;
It comprises: the orbiting piston, the rolling cylinder, the stationary cylinder, the pin mechanism, a casing incorporating the drive source, and the drive transmission unit.
The orbiting piston, the rolling cylinder, and the stationary cylinder constitute a compression unit,
The pin mechanism is fitted into the slide groove,
The swing piston is relatively reciprocally moved in the cylinder groove,
A suction chamber, a compression chamber, and a discharge chamber are formed in the compression unit by the reciprocating motion,
The drive source via the drive transmitting portion, to drive at least the rolling cylinder,
The rolling cylinder positive displacement compressor , wherein the pin mechanism has a slider pair surface slidably contacting the slide groove . The slider even number side is rotatably is installed, the rolling cylinder type displacement type compressor according to claim 1 around the central axis of the pin mechanism. The drive transmission unit has an eccentric shaft.
The eccentric shaft is connected to the pivoting piston,
Said pivoting piston, through said eccentric shaft, driven by the drive source, the rolling cylinder type displacement type compressor according to claim 1 or 2. The rolling cylinder positive displacement compressor according to claim 3 , wherein the turning piston rotates on the central axis of the eccentric shaft as a rotation axis and revolves on the central axis of the drive transmission unit as a rotation axis. The rolling cylinder positive displacement compressor according to claim 4 , wherein the drive transmission part includes a crank shaft. The rolling cylinder positive displacement compressor according to claim 5 , wherein the shaft is provided with a shaft collar, and a portion of the shaft collar is biased to the rolling cylinder. The rolling cylinder positive displacement compressor according to any one of claims 1 to 5 , wherein the drive transmission unit and the rolling cylinder have an integrated configuration.

Images