WO2019167163A1 - Rolling cylinder-type displacement compressor - Google Patents

Abstract

The rolling cylinder-type displacement compressor according to the present invention is provided with: a cylindrical rolling cylinder having a cylinder groove; a revolving piston having a slide groove; a stationary cylinder; a pin structure; a drive source; a drive transmission part connecting the rolling cylinder and the drive source to each other; and a casing in which the revolving piston, the rolling cylinder, the stationary cylinder, the pin structure, the drive source, and the drive transmission part are housed. The revolving piston, the rolling cylinder, and the stationary cylinder constitute a compression part. The pin structure is fitted into the slide groove. The revolving piston relatively reciprocates in the cylinder groove. In the compression part, a suction chamber, a compression chamber, and a discharge chamber are formed by the reciprocation. The drive source drives at least the rolling cylinder via the drive transmission part. Accordingly, collisions between movable compression elements in a rolling cylinder-type displacement compressor are reduced, whereby degradation of performance of the compressor can be suppressed.

Description

Rolling cylinder positive displacement compressor

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

A rolling cylinder positive displacement compressor with a fixed pin mechanism has a geometry in which the two strings drawn to both centers from a given point on a circle passing through the center of the pin mechanism and the center of rotation of the rolling cylinder have a constant angle. It is a unique device that uses scientific relations (the law of constant circumference angle). In this device, compression elements that constitute a compression chamber that compresses a working fluid such as a refrigerant include a stationary cylinder that is a stationary compression element that does not move, and a movable compression element that accompanies movement. The movable compression element includes a rolling cylinder that rotates, and a revolving piston that takes a posture toward the center of the rolling cylinder along with a revolving motion that passes through a circle passing through the center of the rolling cylinder and the pin mechanism.

In these movable compression elements, a compression chamber is formed in cooperation with each other, so that forces act on each other by sliding or the like, and forces act from the working fluid and the support portions of the compression elements by compression of the working fluid. Since the force of the direction which prevents a turning motion from a working fluid acts on a turning piston, the driving force which opposes it becomes essential. On the other hand, the rolling cylinder has a feature that torque that hinders rotational motion from working fluid does not work.

In Patent Document 1, a driving force is applied to a swing piston by a shaft driven by a motor to counteract the force acting on the swing piston from the working fluid, so that the working fluid is compressed, and the 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 that acts on the rolling cylinder is only the friction torque that works from the support portion and the torque that works from the orbiting piston.

By the way, since there is always a gap in the sliding portion between the swing piston and the rolling cylinder, even if the posture where the swing piston is located is taken, the rotation angle of the rolling cylinder that cooperates to form the compression chamber is one. There is always a range of rotation angles that can be incorporated.

Therefore, the rotational speed of the rolling cylinder is inevitably lowered by the friction torque, and the rolling cylinder is shifted to the smaller rotation angle within the range of play, 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, this collision advances rapidly toward the larger rotation angle within the range of play. Then, the same collision is repeated. Furthermore, if this collision becomes extremely intense, it will collide with the revolving piston even when it returns to a place where the rotation angle is large, and a much more severe collision will occur with an extremely short period.

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

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

A rolling cylinder type positive displacement compressor of the present invention includes 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 incorporating a swing piston, a rolling cylinder, a stationary cylinder, a pin mechanism, a drive source and a drive transmission 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 revolving piston relatively reciprocates in the cylinder groove, and the suction portion, the compression chamber, and the discharge chamber are formed in the compression portion by the reciprocation. The drive source drives at least the rolling cylinder through the drive transmission unit.

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

1 is a longitudinal sectional view showing an RC compressor according to Embodiment 1. FIG. 1 is a perspective view illustrating a rolling cylinder of an RC compressor according to Embodiment 1. FIG. 1 is a perspective view showing a turning piston of an RC compressor according to Embodiment 1. FIG. 1 is a perspective view showing a pin mechanism of an RC compressor according to Embodiment 1. FIG. It is a perspective view which shows the other pin mechanism of RC compressor which concerns on Example 1. FIG. FIG. 3 is a flowchart illustrating a compression process of the RC compressor according to the first embodiment. 1 is an exploded perspective view showing an oil supply pump of an RC compressor according to Embodiment 1. FIG. 6 is a longitudinal sectional view showing an RC compressor according to Embodiment 2. FIG. It is the L section enlarged view of FIG. It is the perspective view seen from the upper side of the rolling cylinder of RC compressor concerning Example 2. FIG. It is the perspective view seen from the downward direction of the rolling cylinder of RC compressor which concerns on Example 2. FIG. FIG. 5 is a perspective view showing a turning piston of an RC compressor according to a second embodiment. 6 is a perspective view showing a pin mechanism of an RC compressor according to Embodiment 2. FIG. It is the schematic diagram which looked at the shaft collar part and rolling cylinder contact part of RC compressor concerning Example 2 from the lower side of the shaft. 6 is a perspective view showing a rolling cylinder of an RC compressor according to Embodiment 3. FIG. 1 is a cross-sectional view illustrating an oil supply pump of an RC compressor according to Embodiment 1. FIG. FIG. 6 is an exploded perspective view showing an oil supply pump of an RC compressor according to a fourth embodiment.

The present invention relates to a rolling cylinder type positive displacement compressor having a fixed pin mechanism for defining the attitude of a revolving piston.

Hereinafter, the rolling cylinder type positive displacement compressor (hereinafter also referred to as “RC compressor”) of the present invention will be described in detail with reference to the drawings as appropriate using a plurality of embodiments. In addition, the same part is demonstrated using the same figure in each Example. Moreover, the same code | symbol in the figure of each Example shows the same thing or an equivalent, and the overlapping description is abbreviate | omitted. In addition, the dimension ratio of each element to show in figure shows one Embodiment. Therefore, the size relationship and angle of each dimension in the illustrated shape also indicate an embodiment. Moreover, the part which attached | subjected the code | symbol with a parenthesis in a figure shows the Example which added and removed and changed. In the latter case, the addition or removal is described in the text. Further, specific dimension values are not particularly limited, but it is desirable that the outer diameter of the rolling cylinder type positive displacement compressor is in a range from 10 mm to 2000 mm.

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

The present embodiment in which the rolling cylinder is driven to rotate is an RC compressor of a type in which a slider is provided in a pin mechanism that is a support portion of a swing piston, and a piston drive source that is a drive source of the swing piston is not provided.

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

As shown in the figure, the RC compressor is roughly composed of a compression unit, a motor 7 as a drive source, and an oil storage unit 125.

In this figure, in a casing constituted by a casing cylindrical portion 8a, a casing upper lid 8b and a casing lower lid 8c, a compression portion, a motor 7 serving as a driving source of the compression portion below, a compression portion, A shaft 6 that is a drive transmission unit that connects the motor 7 is disposed. The shaft 6 is arranged in the vertical direction.

The compression unit includes a rolling cylinder 1, a turning piston 3, and a stationary cylinder 2 as components that directly act on the compressed working fluid. The rolling cylinder 1 and the turning piston 3 are movable compression elements. The stationary cylinder 2 is a stationary compression element. The movable compression element and the stationary compression element 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.

Regarding these materials, the cost can be kept low if the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of cast iron. Alternatively, the rolling cylinder 1 may be made of an aluminum alloy, and the turning piston 3 and the stationary cylinder 2 may be made of cast iron. In this way, since the rolling cylinder 1 that rotates passively can be reduced in weight, it is possible to make it difficult for malfunctions to occur and smooth operation. Furthermore, if the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of an aluminum alloy, the entire RC compressor can be reduced in weight.

The compression part has a structure in which the upper part is covered with a stationary cylinder 2 and the lower part is covered with a frame 4. The compression part is fixedly arranged on the casing cylindrical part 8a by welding or the like. The frame 4 is provided with a main bearing 24 including an upper main bearing 24a and a lower main bearing 24b. The shaft 6 is supported by the main bearing 24 in a rotatable state. The frame 4 supports the shaft 6. The shaft 6 protrudes below 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 2b whose center axis is the cylinder rotation axis. The stationary cylinder 2 has a cylinder outer peripheral groove 2m on the outer peripheral side surface thereof. From the upper surface of the stationary cylinder 2, a bypass hole 2e penetrating into the cylinder hole 2b is provided. A pin mechanism 5 is provided on the bottom surface of the cylinder hole 2b. A bypass valve 22 is provided on the upper surface side of the stationary cylinder 2.

In addition, 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 passes through the discharge cover chamber 130 that is a space between the upper surface of the stationary cylinder 2 and the discharge cover plate 230b, and is configured to be swirled into the swirl chamber 140 from the discharge cover port 230a. Yes.

The slide piston 3 is provided with a slide groove 3b. A pin mechanism 5 is inserted into the slide groove 3b. The revolving piston 3 is provided with a piston lower surface hole 3g. The pin mechanism 5 is fitted into the slide groove 3 b of the swing piston 3 and serves as a support portion that regulates the position and posture of the swing piston 3.

The motor 7 is composed of a rotor 7a fixedly disposed on the shaft 6 and a stator 7b fixedly disposed on the casing cylindrical portion 8a. Here, the rotor 7a attached to the shaft 6 is attached to the stator 7b forming the motor 7 while being slightly lowered. This gives an upward axial thrust to the shaft 6.

The oil storage part 125 is an area surrounded by the casing cylindrical part 8a, the casing lower lid 8c, and the sub-frame 35.

At the lower end of the shaft 6, an oil supply pump 200 having a boosting capability is provided. The shaft 6 is provided with a shaft oil supply vertical hole 6b (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 sub horizontal hole 6g, shaft oil supply lower main bearing hole 6f, shaft oil supply upper main bearing hole 6e) connected to the sub bearing 25, the lower main bearing 24b, and the upper main bearing 24a. ing. The upper main bearing 24a is supplied with oil by a shaft oil supply upper main bearing hole 6e and an oil supply main shaft groove 6k.

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

A back chamber 110 which is a back 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 serve as a flow path for the working fluid having a discharge pressure. Furthermore, an oil discharge path 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 introduces a working fluid from the outside to a compression section provided inside the casing 8. The discharge pipe 55 discharges the working fluid pressurized by the compression unit to the outside. The suction pipe 50 and the discharge pipe 55 are provided on the casing upper lid 8b. In addition, a hermetic terminal 220 is provided on the casing upper lid 8b. A motor wire 7b3 is connected to the hermetic terminal 220 so that electric power can be supplied to the stator winding 7b2 of the motor 7 from an external power source (not shown).

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 given with reference to FIG.

The working fluid introduced from the suction pipe 50 is compressed in the compression unit 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, the oil contained in the working fluid adheres to the discharge cover 230 and is separated. The working fluid in which the amount of oil is reduced blows 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 casing upper chamber 120 and is discharged to the outside of the compressor from the discharge pipe 55 provided in the casing upper lid 8b. Note that in the casing upper chamber 120, the flow rate of the working fluid decreases, so that a slight amount of remaining oil mist tends to settle, and the amount of oil contained in the working fluid becomes extremely small.

On the other hand, although there is no main flow of working fluid below the compression section, the working fluid of discharge pressure flows through the cylinder outer circumferential groove 2m and the frame outer circumferential groove 4m, which are outer circumferential grooves of the compression section. . Thereby, the whole casing space including the lower part of a compression part becomes discharge pressure. That is, a high pressure chamber system is realized.

The auxiliary bearing 25 includes a ball 25a and a ball holder 25b that rotatably supports the ball 25a in all directions. After the lower portion of the shaft 6 is inserted into the ball 25a and the ball 25a is mounted on the ball holder 25b, the ball holder 25b is fixedly disposed on the sub-frame 35 welded to the casing cylindrical portion 8a. As a result, the auxiliary bearing 25 is configured to rotatably support the lower portion of the shaft 6.

Note that the RC compressor can be installed with the central axis of the cylindrical casing facing in the horizontal direction (lateral). 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 surrounding hole 35a and the sub-frame central hole 35b of the sub-frame 35, which is a partition of the oil storage part 125, so that an appropriate amount of lubricating oil stays in the oil storage part 125. There is.

The subframe 35 is provided with a subframe peripheral hole 35a and a subframe center hole 35b. Oil returns to the oil reservoir 125 through these holes. An oil supply pump 200 is provided at the lowermost end of the shaft 6 via a pump connecting portion 6z, and feeds oil into a shaft oil supply vertical hole 6b that communicates with each bearing and compression portion.

Also, oil is sealed in the casing at an appropriate stage of assembling the RC compressor, and an oil storage part 125 for storing the oil is formed in the vicinity of the casing lower lid 8c which is the lowermost part.

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

In the present embodiment, the reference numerals 210 and 200 'with parentheses are not adopted.

In this embodiment, the shaft 6 is directly connected to the rolling cylinder 1 of the compression portion. Therefore, the rolling cylinder 1 is directly driven to rotate 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 the portion indicated as the M portion. In other words, the shaft 6 is fixed to the lower surface of the rolling cylinder 1. This integration may be performed from one material, or may be integrated by welding, diffusion bonding, or the like separately processed. In addition, when deformation occurs in integration after processing, finishing may be performed after integration. Furthermore, it is good also as a form which provides a joint in the M part of FIG. 1, and transmits torque. As the joint, an Oldham joint capable of allowing an eccentric deviation, a universal joint capable of allowing a set angle deviation, a spline joint, and the like can be considered.

Since the rotating body of the rolling cylinder 1 integrated with the shaft 6 is balanced at the center of rotation, an unbalanced installation for balancing, which is normally provided, becomes unnecessary.

Next, each element will be explained individually.

FIG. 2 shows 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 1b and a rolling end plate 1a. A shaft 6 is directly connected and fixed to the lower surface of the rolling cylinder 1.

The rolling cylinder 1b has a cylinder groove 1c. The rolling end plate 1a constitutes a bottom surface portion (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 oiling hole 1k is provided at the center of the bottom surface 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 end plate portion 1a1 projecting from the bottom of the cylinder groove 1c to the outer peripheral side of the rolling cylinder 1b. The rolling end plate portion 1a1 is urged against 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. And the rolling outer periphery hole 1f which connects the rolling outer periphery cut part 1g and the side surface of the cylinder groove 1c is provided. Further, a rolling end plate recess 1i is provided at a portion where the rolling outer peripheral cut portion 1g and the upper surface of the rolling end plate portion 1a1 are closest to each other. Thereby, the upper surface of the rolling end plate portion 1a1 is lubricated. The rolling end plate recess 1i is provided so as not to directly contact the outer peripheral portion of the rolling end plate portion 1a1 (to the extent that it does not reach the outer peripheral portion of the rolling end 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 portion collar 1g1 is provided on the upper portion of the rolling outer periphery cut portion 1g. This prevents internal leakage due to communication with a suction groove (not shown) constituting a suction flow path provided on the bottom surface of the cylinder hole 2b of the stationary cylinder 2 facing the rolling cylinder upper surface 1b1, and improves compression performance. be able to.

In this embodiment, 1h, which is a parenthesis, is not adopted.

FIG. 3 shows the details of the swiveling piston 3 of FIG. First, a case where the parenthesized symbols 3b1 and 3b2 are not employed 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. A slide groove 3b is provided on the piston upper surface 3d. The depth of the slide groove 3b is a depth communicating with the piston lower surface hole 3g. The side surface of the orbiting piston 3 is provided with two piston cut surfaces 3c that are parallel to each other and a piston tip surface 3e that connects them. Further, the slide groove 3b has a structure that reaches the piston cut surface 3c, and thereby assumes a function of an oil supply path 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 is inserted into the slide groove 3b of the revolving piston 3 to constitute a pin slide mechanism.

FIG. 4A shows an example of a pin mechanism 5 composed of a slider 5a and a fixed pin 5s.

In this figure, the pin mechanism 5 is disassembled into a slider 5a and a fixed pin 5s.

The slider 5a has a substantially rectangular parallelepiped shape, and has a slider pair face 5a1 that slides with the slide groove 3b (FIG. 3) of the orbiting piston 3. In other words, the slider 5a has a slider mating surface 5a1 slidably contacting the slide groove 3b (FIG. 3). The slider 5a has a slider shaft hole 5a10 and a slider groove 5a2. The slider groove 5a2 is provided on the slider pair 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. The fixed pin 5s is provided with a fixed pin oil supply vertical hole 5s1 and a fixed pin oil supply horizontal hole 5s2. The fixed pin oil supply vertical hole 5s1 has an opening on the lower surface of the fixed pin flange 5s3. The fixed pin oil supply horizontal hole 5s2 has an opening in the side surface portion of the fixed pin 5s, and is connected to the fixed pin oil supply vertical hole 5s1 inside the fixed pin 5s.

The fixing pin 5s is inserted into the slider shaft hole 5a10 of the slider 5a and fixed. The slider 5a is installed in a state where the central axis of the pin mechanism 5 is the rotation axis (a state where the slider 5a is rotatable about the fixed pin 5s). The fixed pin flange 5s3 supports the slider 5a in the axial direction. The fixed pin oil supply vertical hole 5s1 and the fixed pin oil supply horizontal hole 5s2 serve as an oil supply path to the sliding portion between the slider 5a and the fixed pin 5s.

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

This figure shows a state in which the pin mechanism 5 is disassembled into a slider 5a and a 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 coupled to each other, and has a slider mating surface 5a1 that slides on the slide groove 3b (FIG. 3) of the orbiting piston 3. The slider 5a has a slider groove 5a2. The slider groove 5a2 is provided on the slider pair surface 5a1 for lubrication. The slider rotation pin 5a3 is a shaft portion of the slider 5a. Inside the slider 5a, a slider oiling vertical hole 5a4 and a slider oiling horizontal hole 5a5 are provided. Slider oil supply vertical hole 5a4 has an opening in the lower surface of the substantially rectangular parallelepiped portion of slider 5a. The slider oil supply horizontal hole 5a5 has an opening in 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.

Slider oil supply vertical hole 5a4 and slider oil supply horizontal hole 5a5 serve as an oil supply path to the sliding part between slider 5a and pin bearing 5c, and lubricate the bearing part.

In addition, 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 than the configuration of FIG. 4A.

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

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

In this figure, the shaft 6 has a shaft oil supply vertical hole 6b passing through the central axis thereof. The shaft 6 is provided with a shaft oil supply sub horizontal hole 6g which is an oil supply path to the sub bearing 25, a shaft oil supply lower main bearing hole 6f and a shaft oil supply main bearing hole 6e which are oil supply paths to the main bearing 24. It has been. Further, an oil supply main shaft groove 6k extending from the shaft oil supply upper main bearing hole 6e to the back chamber 110 is provided on the side surface of the shaft 6.

Incidentally, as shown in FIG. 2, the upper opening of the shaft oil supply vertical hole 6b is connected to the rolling bottom oil supply hole 1k so as not to generate a leakage flow path. Further, a pump connecting portion 6 z for insertion into the oil supply pump 200 protrudes from the lower end portion of the shaft 6. And the shaft oil supply vertical hole 6b is opening in the center.

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

FIG. 6 is an exploded perspective view showing the fuel pump 200. In FIG. 6, reference numerals 204 ′ and 200 ′ with parentheses are not adopted.

The oil supply pump 200 uses the principle of a rolling cylinder type positive displacement fluid machine, like the above-described compression section. The oil supply pump 200 is configured to function as a pump that does not cause a compression operation because oil having a low vapor pressure is used as the working fluid. In other words, it is not a type in which the refueling revolving piston 203 is driven to rotate, but a type in which the refueling rolling cylinder 201 is rotated coaxially with the shaft 6. As a result, the eccentric shaft for the oil pump required for driving the oil supply swivel piston 203 becomes unnecessary, and there is an effect that the configuration is simplified and the manufacturing cost is reduced.

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

The oil supply pump 200 includes an oil supply stationary cylinder 202, an oil supply rolling cylinder 201, an oil supply swivel piston 203, and an oil supply 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 oil supply turning piston 203 has an oil supply pin groove 203b and an oil supply rear hole 203g.

The oiling lid 204 is provided with an oiling pin 205 at a position off the center. In other words, the oil supply pin 205 is provided at an eccentric position different from the center of the oil supply lid 204. In addition, the oil supply lid 204 has an oil supply discharge groove 204d, an oil supply communication groove 204e, an oil supply suction groove 204s, and an oil supply suction hole 204h. The oil supply communication groove 204e is connected to the oil supply discharge groove 204d and has a shape that surrounds the periphery of the oil supply pin 205 and extends to the center of the oil supply 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 connection portion 6z is passed through the oil supply shaft through hole 202a, and then the pump connection portion 6z is connected to the oil supply shaft. Insert into the connecting hole 201d. Then, after the oil supply swivel piston 203 is fitted into the oil supply cylinder groove 201c, the oil supply pin 205 is covered with an oil supply cover 204 provided eccentrically. Here, the oil supply pin 205 is inserted into the oil supply pin groove 203 b of the oil supply turning piston 203. And finally, it fixes to the sub-frame 35 (FIG. 1) with the three oil supply bolts 209. FIG.

In this embodiment, the fuel pump 200 is assembled and attached to the sub-frame 35 at the same time using the fuel bolt 209. First, after the fuel pump 200 is assembled, the assembly to the sub-frame 35 is performed. It is good also as a two-stage process which performs attachment. Thereby, the assembly accuracy of the assembly is improved, and the high performance of the oil supply pump 200 can be realized.

Next, the operation of the oil 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 oil supply pin 205 is inserted into the oil supply pin groove 203b in the state where the oil supply pump 200 of FIG. 6 is assembled, and an arrow indicates the oil supply rolling cylinder 201 (shaft). 6) the rotation direction.

FIG. 15 shows the timing when the working chamber on the left side of the refueling swivel piston 203 finishes 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 finishes the suction stroke and changes from the oil supply / intake chamber 211 to the oil supply / discharge chamber 212.

By making the oil supply / discharge groove 204d into a crescent shape that extends right below the working chamber on the right side, the compression stroke that occurs in the rolling cylinder type positive displacement compressor does not occur. 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 swivel piston 203 in the oil supply cylinder groove 201c (FIG. 6) also rotates. .

However, as a result of the restriction of the position and posture of the oil supply pin groove 203b by the oil supply pin 205, the oil supply swiveling piston 203 has a turning center at the midpoint of the line connecting the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201. Then, a turning motion is performed in which the distance between the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201 is a turning diameter. Accordingly, the oil supply swivel piston 203 relatively reciprocates in the oil supply cylinder groove 201c with a stroke twice the distance between the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201.

Thereby, the oil in the oil storage part 125 is sucked up from the oil supply suction hole 204h and sent out to the oil supply communication groove 204e. And oil is finally sent into the shaft oil supply vertical hole 6b (FIG. 6) via the oil supply pin groove 203b and the oil supply back hole 203g (FIG. 6).

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

The free piston type system in which the oil supply rolling cylinder 201 is driven to rotate and the oil supply swiveling piston 203 is restricted by the oil supply pin 205 makes assembly extremely easy. In the rolling cylinder method, which is a method of revolving the refueling swivel piston 203, the center axis of the refueling pin and the center axis of the refueling rolling cylinder are on the revolving locus of the refueling swirl piston, and are opposed 180 degrees. Otherwise, the pump will not work and will lock.

However, with this method, considering that the revolving piston relatively reciprocates in the oil cylinder groove, assembly is possible only by managing the center axis of the oil pin within a certain value from the center axis of the oil rolling cylinder. . Thereby, there exists an effect that manufacturing cost can be reduced.

Compared to gear pumps such as trochoid oil pumps, the shape of the components is simple, so high accuracy can be realized at low cost. Improvement in compressor performance due to improved oil pump performance and reduction in manufacturing costs There is an effect that can be realized. 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 supply / discharge amount peak to the load peak in the bearing portion. There is an effect.

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

The working fluid enters the compression section through the suction pipe 50 (FIG. 1) from the suction system outside the RC compressor, and is pressurized by the same compression operation as in Patent Document 1. The pressurized working fluid is ejected from the discharge path (reference numeral 2d in FIG. 5) to the upper portion of the stationary cylinder 2. Under over-compression conditions where the operating pressure ratio is lower than the pressure ratio corresponding to the specific volume ratio of the RC compressor, the working fluid is also ejected from the bypass hole 2e via the bypass valve 22 (FIG. 1).

Then, as shown in FIG. 1, after colliding with the discharge cover plate 230 b of the discharge cover 230 fixedly arranged on the upper part of the stationary cylinder 2, and separating most of the oil contained in the working fluid, it is displaced from the radial direction. From the discharge cover port 230 a provided at an angle approximately along the inner wall of the discharge cover chamber 130, the swirl flows into the swirl chamber 140. There, the oil remaining in the working fluid adheres to and separates from the inner wall of the casing cylindrical portion 8a by centrifugal force. Finally, the oil enters the casing upper chamber 120 while changing the flow direction from the outer peripheral gap of the discharge cover plate 230b at the lower end surface of the casing upper lid 8b, and the oil that could not be separated is separated by the sedimentation action. The pipe 55 exits to the discharge system outside the RC compressor.

As a result, there is no main flow of working fluid flowing into the lower part of the compression part, but since the working fluid of discharge pressure flows through the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m, the entire casing space including the lower part of the compression part is discharged. Pressure.

As will be described in the following description of the oil flow, in particular, since the back chamber 110 on the back surface of the rolling cylinder 1 also has a discharge pressure, the rolling cylinder 1 is urged toward the stationary cylinder 2 while sandwiching the swiveling piston 3 to operate. The axial clearance forming the chamber seal is reduced. The axial clearance includes a clearance between the piston upper surface 3d and the bottom surface of the cylinder hole 2b, a clearance between the piston lower surface 3f and the bottom surface of the cylinder groove 1c, a clearance between the rolling cylinder upper surface 1b1 and the bottom surface of the cylinder hole 2b, There is a gap between the upper surface of the rolling end plate portion 1a1 and the lower surface of the stationary cylinder 2 (around the cylinder hole 2b). Thereby, there exists an effect that sealing performance improves and compressor efficiency improves.

Furthermore, when a familiar coating is provided on these surfaces, the gap is further narrowed, the sealing performance is further improved, and the compressor efficiency is further improved. An example of such a film is a manganese phosphate compound when the material is cast iron. In particular, since the clearance between the upper surface of the rolling cylinder 1b1 and the bottom surface of the cylinder hole 2b and the clearance between the upper surface of the rolling end plate portion 1a1 and the lower surface of the stationary cylinder 2 (around the cylinder hole 2b) are both reduced, Leakage of the working fluid at the discharge pressure to the compression chamber 100 and the suction chamber 95 is greatly reduced, and there is an effect of improving volumetric efficiency and compressor efficiency.

Next, the flow of oil will be explained.

As shown in FIG. 1, the oil in the oil storage part 125 is fed into the shaft oil supply vertical hole 6b through the pump connecting part 6z 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) via the oil supply horizontal hole. Of 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 main shaft groove 6k. The oil that has entered the back chamber 110 is then discharged to the upper surface of the stator 7b through the oil discharge passage 4x and the frame outer peripheral groove 4m. As a result, the back pressure that is the pressure in the back chamber 110 becomes the discharge pressure.

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

Also, 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 that has entered the slide groove 3b lubricates the sliding portion between the pin mechanism 5 and the slide groove 3b, and enters the sliding gap between the revolving piston 3 and the stationary cylinder 2 or the rolling cylinder 1 to provide lubrication and sealing. . The oil that has entered each gap enters the working chamber again and mixes with the working fluid. Then, it is mixed with the working fluid and discharged from the discharge passage 2d to the discharge cover chamber 130.

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

On the other hand, oil that has flowed into the working chamber via various seal gaps is mixed with the working fluid in the working chamber, and when the working fluid enters the leakage passage during the suction, compression, or discharge stroke, An oil film is formed on the inside to suppress internal leakage. Furthermore, since the majority of leak flow paths are locations of relative motion between the compression elements, the oil that flows in reduces friction and improves lubricity. In this way, there is an effect of improving the compressor efficiency. The oil mixed with the working fluid in this way is finally ejected together with the working fluid into the discharge cover chamber 130 as described in the description of the flow of the working fluid, with internal circulation in the working chamber. Separate from fluid. The oil thus separated passes through the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m on the outer periphery of the compression portion and is discharged to the upper surface of the stator 7b in the lower space of the compression portion.

As a result, all of the oil that has risen to the compression portion through the shaft oil supply vertical hole 6b is collected on the upper surface of the stator 7b. Thereafter, it passes through a hole through which the outer stator cut surface 7b1 and the stator winding 7b2 pass, and reaches a space below the motor 7. Thereafter, a small amount passes through the sub-frame peripheral hole 35a and returns to the oil storage part 125 except that the small amount of oil passes through the sub-frame central hole 35b and is supplied to the inner and outer circumferences of the balls 25a of the sub-bearing 25.

Next, with reference to FIG. 5, the compression operation in the compression unit will be explained, and the operational effects of the invention will be explained.

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

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

When the shaft 6 rotates from the upper left shaft rotation angle 0 degree in FIG. 5, a suction groove 2 s <b> 2 in which an upper working chamber at each stage is provided at the bottom of the cylinder hole 2 b (FIG. 1) of the stationary cylinder 2. Or the suction passage 2s of the suction hole 2s1, so that the suction chamber 95 is formed. On the other hand, the working chamber on the opposite side is the compression chamber 100 or the discharge chamber 105. For this reason, a force due to a pressure difference between the two working chambers is applied from the working fluid to the swiveling piston 3.

In FIG. 5, this force vector is indicated by a white arrow described from the compression chamber 100 at each stage toward the swiveling piston 3. Further, the force vector that the slider 5a of the pin mechanism 5 serving as a support portion counteracts against this force exerts on the swing piston 3 is indicated by a black arrow described in the vicinity of the rotation center at each stage.

As is clear from FIG. 5, the lines of action of the two forces are always deviated except for only the shaft rotation angle of 0 degrees. For this reason, the two forces become couples, and the orbiting piston 3 tries to rotate. Since actual element parts always have gaps, minute rotations are actually generated. It can be seen from FIG. 5 that the direction of rotation is always counterclockwise.

Therefore, the orbiting piston 3 comes into contact with the rolling cylinder 1 at a black circle (a boundary corner portion between the piston cut surface 3c and the piston tip surface 3e in FIG. 3). And since the contact location is always the same location as shown in FIG. 5, it turns out that there is no time when contact is lost. Note that contact is not necessary because the force is completely balanced only for a moment when the shaft rotation angle becomes 0 degrees, but in this case, it continues to rotate while maintaining contact due to inertia.

By this contact, the rolling cylinder 1 receives a torque that rotates counterclockwise. However, since the motor 7 that is a cylinder driving source of the rolling cylinder 1 applies a counter torque, the rolling cylinder 1 does not rotate counterclockwise. The compression operation continues.

As a result, the rolling cylinder 1 and the revolving piston 3 are always in contact with each other, so that there is no rotation play between them. As a result, the revolving piston 3 does not collide with the side surface of the cylinder groove 1c of the rolling cylinder 1, so that there is an effect that vibration and noise are reduced. Further, since the impact force does not act 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 front end surface 3e of the swing piston 3 which is the counterpart, the sliding loss. And wear are reduced, and compressor performance and reliability are improved. Furthermore, since the force applied to the pin mechanism 5 that is the support portion of the orbiting piston 3 is not an impact force due to the collision, the reliability of the pin mechanism 5 is improved. Further, the side surface portion of the cylinder groove 1c and the piston cut surface 3c constitute a seal portion. However, since the contact state of both surfaces is stable, a stable oil film is formed and high sealing performance can be realized. Is also suppressed and the compressor performance is improved.

Further, as another modification of the present embodiment, a slide groove wall indicated by reference numeral 3b1 in FIG. 3 may be employed. This connects both ends of the slide groove 3b, and has the effect of increasing the rigidity of the orbiting piston 3. In particular, as in this embodiment, in a rolling cylinder type positive displacement compressor that applies a driving force only to the rolling cylinder 1, the revolving piston 3 to which the working fluid compressive load 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 deepen the slide groove 3b in order to reduce the surface pressure. However, by providing the slide groove wall 3b1, the surface pressure received from the pin mechanism 5 can be lowered without lowering the rigidity of the swing piston 3. It becomes possible. In this modification, the slide groove wall 3b1 is provided with holes for supplying oil to the piston cut surface 3c and the rolling outer peripheral hole 1f so as not to obstruct the oil flow.

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

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

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

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

In this embodiment, a piston rotation source for rotating the revolving piston 3 with a crank shaft is provided together with a cylinder driving source for rotating the rolling cylinder 1. 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 part is different. Accordingly, a main balance 80 is installed at the upper part of the rotor 7a, and a counter balance 82 is installed at the lower part of the rotor 7a. In addition, the shapes of the rolling cylinder 1, the turning piston 3, and the pin mechanism 5 are partially different from those of the first embodiment.

FIG. 8 is an enlarged view of part L in FIG.

FIG. 9 is a perspective view from above of the rolling cylinder 1 of FIG. FIG. 10 is a perspective view from below of the rolling cylinder 1 of FIG. 1h which is a code with parentheses is not adopted.

As shown in FIG. 8, the shaft 6 has a large-diameter shaft collar portion 6c at the upper portion thereof. The upper surface of the shaft collar portion 6c is referred to as a cylinder contact surface 6m. The cylinder contact surface 6m is provided with an eccentric shaft 6a having an eccentric amount that is half the distance between the pin central axis, which is the central axis of the pin mechanism 5, and the cylinder axis. That is, in the present embodiment, the crank shaft is formed by protruding the eccentric shaft 6a.

Furthermore, an opening of a shaft oil supply vertical hole 6b is provided at the upper end of the eccentric shaft 6a, and a shaft oil supply eccentric groove 6h is provided at the outer peripheral surface of the eccentric shaft 6a.

Further, the rolling cylinder 1 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 inserted into the eccentric shaft insertion hole 1d. A shaft collar contact surface 1e shown in FIG. 10 is provided on the rear peripheral edge of the eccentric shaft insertion hole 1d.

The revolving piston 3 rotates with the central axis of the eccentric shaft 6a as a rotation axis and revolves with the central axis of the shaft 6 (drive transmission unit) as a rotation axis.

FIG. 11 is a perspective view showing a revolving piston of the RC compressor of this embodiment.

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

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

As shown in the figure, the pin mechanism 5 is configured to use the fixed pin 5s as in FIG. 4A of the first embodiment. However, the slider mating surface 5a1 has a small area because the load is small. .

Next, the configuration of the compression unit using the elements having the changes from the first embodiment as described above will be described.

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 swing bearing 23 of the swing piston 3.

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

FIG. 13 is a schematic view of this 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 rotation direction of the rolling cylinder 1, the rolling cylinder 1 is driven to rotate without the swiveling piston 3. That is, the motor 7 is also a cylinder drive source. That is, the RC compressor of the present embodiment is configured to simultaneously perform the rotational drive of the rolling cylinder 1 and the turning drive of the turning piston 3 by one motor 7.

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

Although the way in which the force is applied is different, the transition of the working chamber during the operation of the RC compressor is the same as that in the first embodiment shown in FIG. 5, and will be described with reference to FIG.

As shown in FIG. 5, the rotation speed of the rolling cylinder 1 is half of the turning speed of the turning piston 3. Since the rotational speed of the shaft 6 of the present embodiment structurally matches the rotational speed of the revolving piston 3, a deviation from the rotational speed of the rolling cylinder 1 occurs. However, since the rotational torque is transmitted from the shaft 6 to the rolling cylinder 1 by urging the flat plates, it is possible even if there is a difference in rotational speed or rotational center. Further, 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 the urging of the flat plates is sufficient. For this reason, the rotation of the rolling cylinder 1 quickly rotates the movement of the revolving piston 3, and the black circles in FIG. 5 are always in contact with each other to assist the revolving motion of the revolving piston 3 to a slight extent. Then, as is apparent from FIG. 5, since the contact location is always the same location, it can be seen that there is no time when contact is lost. In this example, unlike Example 1, even when the shaft rotation angle is 0 degree, the contact continues at the same location.

As a result, since the rolling cylinder 1 and the revolving piston 3 are always in contact with each other, no rotation play occurs between them, and the same effect as in the first embodiment is obtained.

The only effect of this embodiment is that the main support portion of the orbiting piston 3 is the eccentric shaft 6a, so that the force applied to the pin mechanism 5 which is another support portion is extremely small, and the reliability of the pin mechanism 5 is improved. There is an effect that it is greatly improved. For this reason, as shown in FIG. 12, the slider mating surface 5a1 can be made smaller, the bearing portion can be enlarged, and the reliability can be improved.

In addition, in order to increase 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 is conceivable that the shaft collar contact surface 1e is a surface with a little cast skin. Moreover, it is good also as the pear ground by electric discharge machining etc. Further, a record groove-like groove processing may be performed with a lathe.

Incidentally, the rolling cylinder 1 of the first and second embodiments has a cylinder groove outer peripheral wall 1w. This type has high sealing performance between the working chambers, but the outer surface of the rolling cylinder 1b is pressed against the inner surface of the cylinder hole 2b by the force received from the working fluid (the force opposite to the black arrow in FIG. 5). There is a problem that sliding loss increases.

Therefore, as shown in FIG. 2, FIG. 9, and FIG. The rolling balance hole 1h has a cross-sectional area equivalent to the longitudinal section (rectangular clearance section) of the outer peripheral surface of the rolling cylinder 1b and the inner peripheral surface of the cylinder hole 2b. Thereby, the pressure difference between both sides of the cylinder groove outer peripheral wall 1w is reduced, and the force with which the outer peripheral surface of the rolling cylinder 1b is pressed against the inner peripheral surface of the cylinder hole 2b is reduced. Thereby, a sliding loss can be reduced and there exists an effect that a compressor efficiency improves. Here, since the lower part of the outer peripheral surface of the rolling cylinder 1b is sealed with the back chamber 110 of the discharge pressure by the upper surface of the rolling end plate part 1a1 as described above, there is no adverse effect on the compressor efficiency due to leakage.

The RC compressor according to Example 3 will be described with reference to FIG.

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

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

When the rolling bottom oiling hole 1k is provided, it is the same as the first embodiment.

On the other hand, when it has the eccentric shaft insertion hole 1d, it is the same as that of Example 2.

Descriptions other than the differences from Example 1 or 2 are omitted.

In this embodiment, in both cases, since both ends of the cylinder groove 1c are missing, there is an effect that the processing becomes easy and the manufacturing cost is reduced. Further, when the rolling outer circumferential cut groove 1g2 is provided behind the rolling outer circumferential cut 1g in the rotational direction, the oil flowing in from the rolling outer circumferential hole 1f is held in the space between the working chambers formed on both sides of the swiveling piston 3. This has the effect of suppressing leakage and improving compressor efficiency.

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

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

6, the oil supply pin 205 is fixed to the oil supply lid 204.

In contrast, in this embodiment, a variable capacity lid 204 ′ shown in FIG. 16 is used in place of the oil supply cover 204 of FIG. 6 and a mechanism capable of moving the oil supply pin 205 is incorporated, thereby providing a variable capacity. Is realized.

In the case of a rolling cylinder type oil pump, as shown in FIG. 6, the oil revolving piston 203 is configured such that the position and posture of the oil pin groove 203 b are restricted by the oil pin 205, so that the center of the oil pin 205 and the oil rolling cylinder A turning motion is performed in which the center point of the center 201 is the turning center and the distance between the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201 is the turning diameter. Accordingly, the oil supply swivel piston 203 relatively reciprocates in the oil supply cylinder groove 201c with a stroke twice the distance between the center of the oil supply pin 205 and the center of the oil supply rolling cylinder 201. From this, the displacement of the oil supply pump can be changed by shifting the center of the oil supply pin 205 with respect to the shaft rotation axis which is the center axis of the oil supply rolling cylinder 201.

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

In this embodiment, as shown in FIG. 16, the variable oil supply lid 204 'is constituted by an oil supply passage plate 204a, an oil supply pin base 204b, and an oil supply pin base presser 204c. The oil supply passage plate 204a has an oil supply suction groove 204s, an oil supply discharge groove 204d, and a screw hole. An oil supply pin 205 is installed in the oil supply pin base 204b, and an oil supply pin drive screw hole 204b1 is provided on the lateral tip surface. The oil supply pin base retainer 204c has an oil supply pin slide hole 204c1, an oil supply suction hole 204h, and a screw hole through which the oil supply pin base 204b slides. The oil supply passage plate 204a, the oil supply pin base 204b, and the oil supply pin base presser 204c are overlapped, and an oil supply pin slide screw 210a that is rotationally driven by the oil supply pin slide motor 210 is screwed into the oil supply pin drive screw hole 204b1. The variable oil supply lid 204 ′ thus manufactured is a variable capacity oil supply pump 200 ′ in the same manner as in FIG. 6.

When operating the variable capacity 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 electric power from the outside, and the oil supply pin base 204b is slid. Thereby, the oil supply pin 205 can be moved and the capacity | capacitance of an oil supply pump can be changed freely. As a result, it is possible to optimize the amount of oil supply under various operating conditions, such as the disadvantage of the oil pump being excessively oiled when the rotational speed is high can be solved by reducing the capacity of the oil pump. . As a result, the compressor efficiency under various operating conditions can be improved.

Hereinafter, the effects of the present invention will be described together.

According to the present invention, among the movable compression elements that cooperate to form a compression chamber, a swiveling piston in which a large force is applied from the working fluid by applying a rotational drive torque to a rolling cylinder that does not receive torque from the working fluid. The swivel angle shifts to the smallest range of play with the rolling cylinder. And finally, it will collide with a rolling cylinder and a sliding part. However, since a large force is acting on the swivel piston in the direction of reducing the swivel angle from the working fluid, the swivel piston does not advance at a stroke even by this collision, and always contacts the rolling cylinder, Continuing the swivel motion against the force from the working fluid.

As a result, collision at the sliding part is avoided, vibration noise and wear are suppressed, and reliability is improved. In addition, the impact load on the sliding part is suppressed, reducing the sliding loss by reducing the sliding load, and the oil film formation by stabilizing the sliding part seal gap can reduce the leakage loss, improving the compressor performance. Can be achieved.

1: rolling cylinder, 1a: rolling end plate, 1a1: rolling end plate, 1b: rolling cylinder, 1b1: rolling cylinder top surface, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 1e: shaft collar contact surface, 1f: rolling Outer peripheral hole, 1 g: Rolling outer peripheral cut portion, 1 g1: Rolling outer peripheral cut portion collar, 1 g2: Rolling outer peripheral cut groove portion, 1h: Rolling balance hole, 1i: Rolling end plate recess, 1k: Rolling bottom oil supply hole, 1w: Cylinder groove outer peripheral wall 2: stationary cylinder, 2b: cylinder hole, 2d: discharge path, 2e: bypass hole, 2m: cylinder outer groove, 2s: suction path, 2s1: suction hole, 2s2: suction groove, 3: revolving piston, 3a: revolving Bearing hole, 3b: slide groove, 3b1: slide groove wall, 3b2: slide groove digging, 3c Piston 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 mating surface, 5a2: Slider groove, 5a3: Slider rotation pin, 5a4: Slider oil supply vertical hole, 5a5: Slider oil supply horizontal hole, 5a10: Slider shaft hole, 5s: Fixed pin, 5s1: Fixed pin oil supply vertical hole, 5s2: Fixed pin lubrication horizontal hole, 5s3: Fixed pin flange, 5c: Pin bearing, 6: Shaft, 6a: Eccentric shaft, 6b: Shaft lubrication vertical hole, 6c: Shaft flange, 6e: Shaft lubrication upper main bearing hole, 6f: Shaft lubrication Lower main bearing hole, 6g: Shaft oiling auxiliary horizontal hole, 6h: Shaft oiling eccentric groove, 6k: Oiling main shaft groove, 6m: Cylinder Touch surface, 6z: pump connection portion, 7: motor, 7a: rotor, 7b: stator, 7b1: stator cut surface, 7b2: stator winding, 7b3: motor wire, 8a: casing cylindrical portion, 8b: casing upper lid, 8c: Casing lower lid, 22: Bypass valve, 23: Slewing bearing, 24: Main bearing, 24a: Upper main bearing, 24b: Lower main bearing, 25: Sub bearing, 25a: Ball, 25b: Ball holder, 35: Sub Frame, 35a: Sub-frame peripheral hole, 35b: Sub-frame 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 storage section, 130: discharge cover chamber, 140: swirl chamber, 200: oil supply Pump, 200 ′: Variable displacement oil pump, 201: Oil rolling cylinder, 201c: Oil cylinder groove, 201d: Oil shaft connecting hole, 202: Oil stationary cylinder, 202a: Oil shaft through hole, 202b: Oil cylinder hole, 203: Oil supply swirling piston, 203b: oil supply pin groove, 203g: oil supply back hole, 204: oil supply cover, 204 ': variable oil supply cover, 204a: oil supply path plate, 204b: oil supply pin base, 204b1: oil supply pin drive screw hole, 204c: Oil supply pin base holder, 204c1: Oil supply pin slide hole, 204d: Oil supply discharge groove, 204e: Oil supply communication groove, 204h: Oil supply suction hole, 204s: Oil supply suction groove, 205: Oil supply pin, 209: Oil supply bolt, 210: Oil supply pin Slide motor, 210a: lubrication pin slide screw, 211: lubrication Included chamber, 212: oil supply discharge chamber, 220: hermetic terminal, 230: discharge cover, 230a: discharge cover openings, 230b: discharge cover plate.

Claims (8)

1. A cylindrical rolling cylinder having a cylinder groove;
   A swivel piston having a slide groove;
   A stationary cylinder;
   A pin mechanism;
   A driving source;
   A drive transmission unit connecting the rolling cylinder and the drive source;
   A casing containing the revolving piston, the rolling cylinder, the stationary cylinder, the pin mechanism, the drive source, and the drive transmission unit;
   The swiveling piston, the rolling cylinder and the stationary cylinder constitute a compression part,
   The pin mechanism is inserted into the slide groove,
   The orbiting piston relatively reciprocates in the cylinder groove,
   In the compression part, a suction chamber, a compression chamber and a discharge chamber are formed by the reciprocating motion,
   The driving source is a rolling cylinder positive displacement compressor that drives at least the rolling cylinder via the drive transmission unit.
2. 2. The rolling cylinder type positive displacement compressor according to claim 1, wherein the pin mechanism has a slider mating face slidably contacting the slide groove.
3. The rolling cylinder type positive displacement compressor according to claim 2, wherein the slider mating surface is rotatably installed around a central axis of the pin mechanism.
4. The drive transmission unit has an eccentric shaft,
   The eccentric shaft is connected to the orbiting piston;
   The rolling cylinder positive displacement compressor according to any one of claims 1 to 3, wherein the revolving piston is driven by the drive source via the eccentric shaft.
5. The rolling cylinder positive displacement compressor according to claim 4, wherein the revolving piston rotates around the central axis of the eccentric shaft as a rotation axis and revolves around the central axis of the drive transmission unit as a rotation axis.
6. The rolling cylinder type positive displacement compressor according to claim 5, wherein the drive transmission unit includes a crank type shaft.
7. The rolling cylinder type positive displacement compressor according to claim 6, wherein the shaft is provided with a shaft collar portion, and a part of the shaft collar portion is biased by the rolling cylinder.
8. The rolling cylinder type positive displacement compressor according to any one of claims 1 to 6, wherein the drive transmission unit and the rolling cylinder have an integrated configuration.

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