JP2021116709A - Rotary type cylinder device - Google Patents

Abstract

To provide a rotary cylinder device capable of efficiently cooling a high-pressure fluid without expanding the physical constitution of a case body.SOLUTION: In a rotary type cylinder device, rotations of an input/output shaft pivoted in a case body in a rotatable manner are converted into reciprocating motions of a plurality of piston sets which are disposed orthogonally to an eccentric cam, in accordance with the principle of inner cycloid, a fluid from the outside is sucked into a cylinder chamber inside of the case body and a compressed fluid is discharged from the cylinder chamber. Cooling channels 8a in which annular channel covers are mounted and a cooling medium flows annularly are formed in outer peripheries of a plurality of cylinders assembled to the case body in which the plurality of piston sets are inserted in a slidable manner. The case body comprises a cooling structure in which the cooling medium taken from an inflow port is passed through the cooling channel which is provided in at least one cylinder outer periphery, and discharged from an outflow port.SELECTED DRAWING: Figure 10

Description

The present disclosure relates to a rotary cylinder device that converts a rotary motion of an input / output shaft into a linear reciprocating motion of a piston in a cylinder.

For example, in a positive displacement fluid compressor, various compressors such as a reciprocating type, a scroll type, a rotary type, a diaphragm type, and a vane type are used. These are designed to suck outside air into the air compression section inside the cylinder, compress it, and discharge the compressed air to the outside of the device.

In a fluid compressor, when the fluid in the cylinder chamber is compressed, the peripheral portion generates heat and becomes hot. Therefore, cooling fins are provided on the outside of the cylinder, and the compressed air is cooled by winding the refrigerant pipe (see Patent Document 1: Japanese Patent Application Laid-Open No. 2004-340915).
In addition, in order to improve the cooling function of the discharged fluid without increasing the physique of the compressor, a compressor equipped with an intercooler core that cools the air discharged to the discharge chamber to mitigate pressure fluctuations has also been proposed. (Patent Document 2: Japanese Patent Application Laid-Open No. 2015-21384).

Japanese Unexamined Patent Publication No. 2004-340955 Japanese Unexamined Patent Publication No. 2015-21384

In each of the above-mentioned compressors, a cooling fin and a refrigerant pipe are provided outside the cylinder (Patent Document 1), and an intercooler core is provided in the discharge chamber (Patent Document 2), so that the high-pressure fluid is cooled. The cooling device is large-scale, the installation area of the device is large, and the cooling efficiency is also lowered.

The present invention has been made to solve the above problems, and an object of the present invention is a small rotary cylinder device capable of efficiently cooling a high-pressure fluid without expanding the body shape of the case body. Is to provide.

The present invention, which is applied to some embodiments described below, comprises at least the following configurations. The rotation of the input / output shaft rotatably supported by the case body is converted into the reciprocating motion of a plurality of piston sets arranged orthogonally to the eccentric cam according to the principle of the inner cycle, and the fluid is supplied from the outside into the case body. This is a rotary cylinder device that sucks fluid into the cylinder chamber and discharges the compressed fluid from the cylinder chamber. Each of the annular flow path covers is attached to form a cooling flow path through which the cooling medium flows in an annular shape, and the case body is provided with a cooling medium taken in from the inflow port on at least one cylinder outer circumference. It is characterized by having a cooling structure that passes through a cooling flow path and is discharged from an outlet.
According to the above configuration, the case body is provided with a cooling structure in which the cooling medium taken in from the inflow port passes through the cooling flow path provided on the outer periphery of at least one cylinder and is discharged from the outflow port. The cooling structure can be provided without increasing the installation area of the main body, and the cooling efficiency is also improved by passing the cooling medium around the outer circumference of the cylinder through the cooling flow path provided.

The case body is composed of a combination of a first case and a second case, and the cooling structure includes a cooling flow path provided on the outer periphery of the plurality of cylinders and a first communication flow path provided in the first case. And the second connecting flow path provided in the second case are connected in parallel, and the cooling medium taken in from the inflow port of the first case is connected in parallel via the first connecting flow path. It may be guided to the second connecting flow path through the cooling flow path on the outer periphery of the plurality of cylinders and discharged from the outlet provided in the second case.
As a result, the cooling medium that has flowed in from the inflow port of the first case flows in parallel from the first connecting flow path through the cooling flow paths on the outer periphery of the plurality of cylinders, and is discharged from the outflow port via the second connecting flow path. The flow path from when the cooling medium flows into the case body to when it is discharged is short, and cooling can be performed efficiently. In this case, considering the flow of the cooling medium in the case body, it is preferable to arrange the first case downward and the second case upward in order to improve the cooling efficiency.

The case body is composed of a combination of a first case and a second case, and the cooling structure includes a first connecting flow path provided in the first case or a second connecting flow path provided in the second case. The cooling channels provided on the outer periphery of the plurality of cylinders are connected in series to each other, and the cooling medium taken in from the inflow port provided in either the first case or the second case is provided. It may be discharged from the outlet provided in either the first case or the second case through the cooling flow path on the outer periphery of the plurality of cylinders connected in series.
As a result, since the cooling flow paths on the outer periphery of the plurality of cylinders are connected in series via the first connecting flow path or the second connecting flow path, the cooling flow flows from the inflow port provided in the first case or the second case. Since the cooling medium always passes through the cooling passages provided on the outer periphery of all the cylinders before being discharged from the outlet, the high-pressure fluid in the case body can be reliably cooled. In this case, the flow of the cooling medium is not affected by the installation posture of the case body, so that the degree of freedom in assembling the device is improved.

A heat radiating member may be used for the cylinder cover that covers the cylinder head that closes the openings of the plurality of cylinders.
As a result, it is possible to improve the heat dissipation and the cooling efficiency through the cylinder cover together with the case body and the cooling medium that circulates around the cylinder.

It is possible to provide a rotary cylinder device capable of efficiently cooling a high-pressure fluid without expanding the body shape of the case body.

It is a perspective view of the rotary type cylinder device. FIG. 1 is a front view of the rotary cylinder device of FIG. 1, a cross-sectional view of arrows XX, and an enlarged cross-sectional view of a cylinder portion. It is an exploded perspective view of the rotary type cylinder device of FIG. FIG. 1 is an axial cross-sectional view of a rotary cylinder device and a partially enlarged cross-sectional view of a case body of FIG. FIG. 1 is a plan view of the rotary cylinder device of FIG. 1, a cross-sectional view in the direction of arrows ZZ, and an explanatory view of a cylinder recovery flow path. FIG. 1 is a front view of the rotary cylinder device of FIG. 1 and a cross-sectional view taken along the line PP. It is a perspective view of the rotary type cylinder apparatus which concerns on another example. FIG. 7 is a front view of the rotary cylinder device of FIG. 7 and a cross-sectional view taken along the line QQ. 7 is a front view, a perspective view, a cross-sectional view in the direction of arrows SS, and a cross-sectional view in the direction of arrows RR in a state where the cylinder and the rotation mechanism portion of the rotary cylinder device of FIG. 7 are removed. The plan view of the first case and the second case, the explanatory view showing the flow path of the coolant of the rotary cylinder device of FIG. 1, the plan view of the first case and the second case, and the cooling of the rotary cylinder device of FIG. It is explanatory drawing which shows the flow path of a liquid. It is a front view of the assembly side of a cylinder to a case body, and the cross-sectional view in the direction of arrow YY. It is a partially broken front view, left side view, and right side view of the flow path cover on the outer periphery of the cylinder. It is a front view, the cross-sectional view in the arrow YY direction, the rear view, and the cross-sectional view in the direction of arrow XX of a cylinder head part (single component). It is a front view, a right side view, a bottom view, and a perspective view of a head cover. It is a schematic diagram which shows the relationship between the rotation trajectory of the first crankshaft centering on an input / output shaft, the rotation trajectory of a second crankshaft centering on the first crankshaft, and the linear reciprocating motion of a double-headed piston set.

Hereinafter, an embodiment for carrying out the invention will be described in detail with reference to the accompanying drawings. First, a rotary cylinder device used for a fluid pump will be mainly described with reference to FIGS. 1 to 15. The rotary cylinder device is assumed to be a device in which the linear reciprocating motion of the piston with respect to the cylinder and the rotational motion of the input / output shaft are mutually converted and input / output. Specifically, a rotary type that converts the rotation of the input / output shaft, which is rotationally driven by a drive source such as a motor, into the reciprocating motion of a pair of double-headed pistons arranged orthogonally to the eccentric cam according to the principle of internal cycloid. It is equipped with a cylinder device.

In the following, a compressor that sucks air from the outside, compresses it, and discharges it will be described as an example. As shown in FIG. 1, the case body 1 is formed by combining the first case 4 and the second case 5. An air import joint 2a is connected to the case body 1 (second case 5), and air is sucked into the cylinder chamber inside the case body 1 from the outside. Further, an air outport joint 2b is connected to the case body 1 (first case 4), and compressed air is discharged from the cylinder chamber. Since the air flow path in the case body 1 is not a main part of the present invention, the description thereof will be omitted.

As will be described later, the case body 1 takes in a cooling medium from the cooling import joint 3a (inflow port), passes through at least one cooling flow path provided on the outer periphery of the cylinder, and passes through the cooling outport joint 3b (cooling outport joint 3b (inflow port). It has a cooling structure that is discharged from the outlet). The cooling import joint 3a (inflow port) and the cooling outport joint 3b (outlet) are pipe-connected to a cooling medium circulation system (not shown). The cooling medium is sent into the case body 1 from the cooling medium circulation system through the cooling import joint 3a. The cooling medium is sent from the case body 1 to the cooling medium circulation system through the cooling outport joint 3b. As the cooling medium, antifreeze, water, oil or the like having a relatively large specific heat is used depending on the application. Further, the circulation system of the cooling medium may be provided with an external liquid feed pump, a heat exchanger (radiator), or the like, or the import joint 3a for cooling by opening and closing the valve using the fluid pressure of tap water or the like. The liquid may be sent from the (inflow port) into the case body 1 and discharged from the cooling outport joint 3b (outlet).

Here, the configuration of the rotary cylinder device housed in the case main body 1 will be described with reference to FIGS. 3 and 4A. In FIG. 4A, the case body 1 is configured by combining the first case 4 and the second case 5 (see FIG. 1), and the input / output shafts are rotatably supported on the case body 1. The input / output shaft is divided into a first input / output shaft 6a and a second input / output shaft 6b. In the first case 4 and the second case 5, the fixing screws 7a and 7b (see FIG. 3) are provided in the screw holes provided at the shaft ends of the guide shaft 28 to be assembled into the screw holes 4a and 5a provided at the four corners, respectively. Each is fitted and assembled integrally. The ends of the first input / output shaft 6a and the second input / output shaft 6b are supported by being exposed from through holes provided in the end faces of the first case 4 and the second case 5, respectively.

The cylindrical cylinder 8 is arranged to face the four side surfaces of the case body 1. In the present embodiment, the case main body 1 is sandwiched and held between the first case 4 and the second case 5 on each side surface. Further, the openings of the cylinder 8 provided on the four side surfaces of the case body 1 are closed by the cylinder head portion 9 and the head cover 10, respectively. Each cylinder head portion 9 is screwed and fixed to the side surface of the case body 1 (first case 4 and second case 5) together with the head cover 10 with fixing screws 11 (see FIG. 3).

As shown in FIG. 3, an O-ring 12a and an O-ring 12b are formed in an annular shape on the inner surface (upper surface of FIG. 3) of the first case 4 from the inside in the radial direction. Arranged on both sides, the first annular flow path cover 13a is fixed by the fixing screw 4i, and the first annular flow path 4b is closed (see FIG. 4A). Further, on the outer surface (lower surface of FIG. 3) of the first case 4, the first end surface cover 4c is screwed and fixed by a fixing screw 4d (not shown) to form a flow path for compressed air.

Similarly, on the inner surface (lower surface of FIG. 3) of the second case 5, O-rings 12a and O-rings 12b are arranged on both sides of the second annular passage 5b (second connecting passage) formed in an annular shape from the inside in the radial direction. The second annular flow path cover 13b is fixed by the fixing screw 5i, and the second annular flow path 5b is closed (see FIG. 4B). Further, on the end surface (upper surface of FIG. 3) of the second case 5, the second end surface cover 5c is screwed and fixed by the fixing screw 5d to form a flow path for compressed air.

As shown in FIG. 4A, the first input / output shaft 6a is rotatably supported in the first case 4 via the first bearing 14a. In the second case 5, the second input / output shaft 6b is rotatably supported via the first bearing 14b. The first input / output shaft 6a is integrally assembled with the first balance weight 15a. Further, the second input / output shaft 6b is integrally assembled with the second balance weight 15b. The first and second balance weights 15a and 15b are between rotating parts centered on the input / output shafts (first input / output shaft 6a and second input / output shaft 6b) including the first crankshaft 16 and the piston unit P, which will be described later. It is provided to balance the mass (static balance) of.

In FIG. 4A, the first crankshaft 16 is provided eccentrically with respect to the axes of the first and second input / output shafts 6a and 6b. Specifically, one end (lower end of FIG. 4A) of the first crankshaft 16 is integrally screwed and fixed by the fixing screw 17b in a state where the first balance weight 15a is fitted and the pin 17a is inserted. Similarly, the other end (upper end of FIG. 4A) of the first crankshaft 16 is integrally screwed and fixed by the fixing screw 17d in a state where the first crankshaft 16 is fitted into the second balance weight 15b and the pin 17c is inserted.

As shown in FIG. 4A, a tubular eccentric cam 18 that can rotate relative to the first crankshaft 16, a first piston set 19 and a second piston set 20 with respect to the eccentric cam 18 (hereinafter, these are referred to as “pistons”. Unit P ") is assembled so that it can rotate relative to each other. The piston set refers to a piston in which a seal cup, a seal cup holding member, a piston ring, and other sealing materials are integrally assembled to the piston head portion of the piston alone.

In the eccentric cam 18, cam portions 18b eccentric with respect to the tubular hole 18a through which the first crankshaft 16 serving as the center of rotation is inserted are continuously formed on both sides in the axial direction. The axis of the cam portion 18b coincides with the second crankshaft (see FIGS. 15: 24a and 24b). Bearing holders 21a and 21b are press-fitted on both sides of the first crankshaft 16 or are bonded to the cylinder hole wall and assembled. The second bearings 22a and 22b are housed in the bearing holders 21a and 21b, and are assembled to both ends of the eccentric cam 18 by inner ring adhesion. The second bearings 22a and 22b rotatably support the eccentric cam 18 relative to the first crankshaft 16. The first crankshaft 16 is the center of relative rotation of the eccentric cam 18.

In the present embodiment, the first piston set 19 and the second piston set 20 are arranged (orthogonally arranged) on the outer periphery of the pair of cam portions 18b of the eccentric cam 18 so as to be relatively rotatable via the third bearings 23a and 23b. ing. Therefore, the second crankshafts are present at positions that are 180 degrees out of phase with respect to the first crankshaft 16. For example, a stainless steel-based metal material is used for the eccentric cam 18, and the eccentric cam 18 is integrally molded by MIM (metal injection mold).

In the piston unit P described above, the portions (first balance weight 15a, second balance weight 15b) that connect the first input / output shaft 6a, the second input / output shaft 6b, and the axis of the first crankshaft 16 are first. It becomes a crank arm. Further, a portion connecting the first crankshaft 16 and the second crankshaft (the axis of the cam portion 18b) between the axes is the second crank arm.

Here, the rotational motion of the first crankshaft 16 and the second crankshafts 24a and 24b centered on the input / output shafts (first input / output shaft 6a and second input / output shaft 6b) and the linear reciprocating motion of a plurality of piston sets. The outline of the principle of (inner cycloidal motion) will be described with reference to FIGS. 15A to 15D. 15A to 15D schematically show a state in which the first crankshaft 16 is rotated by 90 ° in the counterclockwise direction according to the rotation of the first input / output shaft 6a and the second input / output shaft 6b existing in the center O. It is shown. When the first crankshaft 16 rotates around the center O (first input / output shaft 6a, second input / output shaft 6b) due to the rotation of the first input / output shaft 6a and the second input / output shaft 6b, the second crankshaft 24a , 24b reciprocate on the diameter R1 of the rolling circle 26 of the virtual circle 25, and the second crankshafts 24a and 24b reciprocate on the diameter R2 of the rolling circle 26.

That is, the first crankshaft 16 and the eccentric cam 18 (the first crankshaft 16 and the eccentric cam 18 along the rotating track 27 in the counterclockwise direction with a radius r centered on the axis (center O) of the first input / output shaft 6a and the second input / output shaft 6b ( Of the piston sets connected to the eccentric cams 18 having the second crankshafts 24a and 24b as the axial centers, the first piston set 19 passes through the third bearing 23a (see FIG. 4A) due to the rotational movement of FIG. 4A). The second piston set 20 repeatedly reciprocates on the diameter R1 of the rolling circle 26 (concentric circle centered on the axis O) having a radius of 2R while rotating relatively, and the second piston set 20 passes through the third bearing 23b (see FIG. 4A). The reciprocating motion is repeated on the diameter R2 of the rolling circle 26 having a radius of 2R while rotating relatively. In an actual device, the eccentric cam 18 rotates relative to the first crankshaft 16 via the second bearings 22a and 22b, and the first piston set 19 and the second piston set 20 pass through the third bearings 23a and 23b. The pistons 8 are reciprocated while rotating relative to each other.

With the above configuration, the turning radius of the first crank arm connecting the axis (center O) of the input / output shaft and the first crankshaft 16 is R, and the second connecting the first crankshaft 16 and the second crankshafts 24a and 24b. By setting the length of the crank arm to be the turning radius R of the cam portion 18b, the eccentric cam 18 and the first and second piston sets 19, 20 (piston unit P) are set around the first crankshaft 16. It can be compactly assembled in the case body 1 in the axial direction and the radial direction (see FIG. 3).

In FIG. 2B, the first piston head portion 19b and the second piston head portion 20b are formed at both ends in the longitudinal direction of the first and second piston bodies 19a and 20a. Ring-shaped seal cups 19c and 20c and seal cup holding members 19d and 20d (see FIG. 3) are assembled to the first piston head portion 19b and the second piston head portion 20b by fixing screws, respectively. For the seal cups 19c and 20c, an oil-free sealing material (for example, PEEK (polyetheretherketone) resin material or the like) is used.

In FIG. 2B, in the boss hole of the boss portion provided in the first case 4, there are four guide shafts 28 arranged in parallel with the input / output shafts (first input / output shaft 6a, second input / output shaft 6b). Each is fitted in the place. On each guide shaft 28, a first guide bearing 29 that receives the lateral pressure of the first piston body 19a and a second guide bearing 30 that receives the lateral pressure of the second piston body 20a are coaxially assembled so as to be separated in the axial direction. .. As shown in FIG. 3, each guide shaft 28 holds both shaft ends at a corner portion where the first piston body 19a and the second piston body 20a intersect in the case body 1, and the first guide bearing 29 is the first. The second guide bearing 30 is in contact with both side portions of the one piston body 19a, and the second guide bearing 30 is in contact with both side portions of the second piston body 20a for assembly.

13A to 13D show an example of the cylinder head portion 9 (single component diagram; see FIG. 3). The cylinder head portion 9 is formed with a suction flow path for sucking air and a discharge flow path for discharging air in the cylinder chamber 31 (see FIG. 2B) of the cylinder 8. The detailed air flow path in the case body 1 will not be described. The cylinder bed portion 9 is mounted via the flow path on the first case 4 side and the O-ring 12c (see FIG. 3).

As shown in FIGS. 13A, B, and D, a concave groove 9e is provided on one end side (left end side of FIG. 13B) of the cylinder head portion 9 in a circumferential manner. An O-ring 12d (see FIG. 3) is fitted into the concave groove 9e, and the O-ring 12d is fitted by being sandwiched between the cylinder head portion 9 and the head cover 10 (see FIG. 15) (see FIG. 3). As shown in FIGS. 14A to 14D, the head cover 10 is fixed to the wall surface of the case body 1 by screw fitting by inserting the fixing screws 11 into the screw holes 10a provided at six places (see FIG. 3). The head cover 10 can also be used as a heat radiating plate by using a metal plate such as an aluminum plate. Further, the head cover 10 can increase the surface area by bending the metal plate and improve the heat dissipation property.

Next, the cooling structure of the case body 1 will be described.
In FIG. 2B, a cooling flow path 8a is provided around the outer periphery of the cylinder 8. As shown in FIGS. 11A and 11B, the cylinders 8 provided at four locations are formed in a tubular shape, and ridges 8b and 8c protruding outward are provided on the outer peripheral surface in a circumferential manner. The concave groove portion 8d formed between the ridge portions 8b and 8c is used as the cooling flow path 8a. As shown in FIG. 2C, an annular flow path cover 32 that covers the concave groove portion 8d is fitted on the outer periphery of the cylinder 8. As a result, the concave groove portion 8d becomes a sealed cooling flow path 8a. As the flow path cover 32, for example, one molded from resin may be used, or an annular metal member may be used.

In FIGS. 12A to 12C, the flow path cover 32 is formed with a pair of protrusions 32a and 32b having a large outer diameter at a portion formed in an annular shape facing in the radial direction. The protrusion 32a is provided with an inflow port 32c into the cooling flow path 8a of the cooling medium, and the protrusion 32b is provided with an outflow port 32d from the cooling flow path 8a of the cooling medium. The inflow port 32c communicates with the first annular flow path 4b of the first case 4 via the O-ring 12e, and the outlet 32d communicates with the second annular flow path 5b of the second case 5 via the O-ring 12e. (See FIGS. 3 and 6B). In the flow path cover 32, the inflow port 32c and the outflow port 32d are arranged so as to be in point-symmetrical positions (see FIGS. 5B, C and 12C).

As shown in FIG. 2C, the flow path cover 32 is sealed with the O-ring 12f sandwiched between the flow path cover 32 and the outer periphery (projection portion 8b) of the cylinder 8. Further, the opening of each cylinder 8 is closed by assembling the cylinder head portion 9, and the cylinder chamber 31 is formed. An O-ring 12g is sandwiched and sealed between the cylinder head portion 9 and the flow path cover 32, and an O-ring 12h is sandwiched and sealed between the cylinder 8 and the cylinder head portion 9. A peripheral groove 32e into which the O-ring 12g is fitted is formed at an end portion of the flow path cover 32 that overlaps with the cylinder head portion 9 (see FIGS. 12A and 12B).

The flow of the cooling medium in the case body 1 will be described with reference to FIGS. 6A and 6B. FIG. 6 shows the configuration of the first case 4, but the configuration of the second case 5 combined with this is the same, so the illustration is omitted. As shown in FIG. 6A, the cooling medium flows into the first case 4 from the cooling import joint 3a provided in the case body 1 (first case 4). In FIG. 6B, the cooling import joint 3a flows into the first annular flow path 4b (see FIGS. 4A and 4B) formed in an annular shape through the first case inflow path 4e, and flows in all directions from the first annular flow path 4b. It flows so as to orbit the cooling flow path 8a provided on the outer periphery of the cylinder 8 through the first case outflow path 4f to be connected. For example, as shown in FIG. 5C, the cooling medium enters the cooling flow path 8a from the inflow port 32c provided in the flow path cover 32, cools the cylinder 8 while making a half turn on both sides, and then second from the outflow port 32d. It flows out into Case 5. The cooling medium flows into the second annular flow path 5b (see FIGS. 4A and 4B) formed in an annular shape through the second case inflow passage 5e (see FIG. 10A) provided in the second case 5. Then, it flows out from the second annular flow path 5b through the second case outflow path 5f (see FIG. 10A) from the cooling outport joint 3b (see FIG. 6A). The cooling medium may be cooled again by the circulation mechanism and returned to the case body 1, or when the cooling import joint 3a is connected to the water supply via a valve, the cooling outport joint 3b may be used. The spilled water may be drained.

The above flow of the cooling medium is shown by a thick arrow in the schematic diagram shown in FIG. 10A, and together with a plan view showing the first annular flow path 4b of the first case 4 and the second annular flow path 5b of the second case 5, respectively. show. In this case, the cooling medium flowing through the case body 1 is connected to the first case 4 to which the cooling import joint 3a is connected, the cylinders 8 (cooling flow paths 8a) provided on the four surfaces, and the cooling outport joint 3b. The outer circumferences of the plurality of cylinders 8 flow in parallel in the order of the second case 5. As a result, the cooling medium flowing in from the cooling import joint 3a of the first case 4 flows in parallel from the first annular flow path 4b through the cooling flow paths 8a on the outer periphery of the plurality of cylinders 8 and passes through the second annular flow path 5b. Since it is discharged from the cooling outport joint 3b, the flow path from the flow into the case body 1 of the cooling medium to the discharge is short, and cooling can be performed efficiently. In this case, considering the flow of the cooling medium in the case body 1, it is preferable to arrange the first case 4 downward in the vertical direction and the second case 5 upward in the vertical direction in order to improve the cooling efficiency. ..

According to the above configuration, the cooling medium is taken into the case body 1 from the cooling import joint 3a via the first annular flow path 4b, and passes through the cooling flow path 8a provided on the outer periphery of at least one cylinder 8. Since the cooling structure is provided so as to discharge the cooling from the cooling outport joint 3b via the second annular flow path 5b, the cooling structure can be provided without increasing the installation area of the apparatus main body, and the cooling medium is the cylinder 8. The cooling efficiency is also improved by passing through the cooling flow path 8a provided around the outer circumference.

Next, another example of the cooling structure of the case body 1 will be described with reference to FIGS. 7 to 10B. Since the configuration of the rotary cylinder device is the same, the same members will be assigned the same number and the description will be referred to, and the differences in the flow paths of the cooling medium will be mainly described below.
As shown in FIG. 7, an air import joint 2a is connected to the case body 1 (second case 5), and air is sucked into the cylinder chamber inside the case body 1 from the outside. Further, the case main body 1 (first case 4) is similarly connected to the air outport joint 2b, but the flow path of the cooling medium is different as described below.

A cooling import joint 3a (inflow port) and a cooling outport joint 3b (outflow port) are connected to the second case 5, which is the same as the case body 1. The cooling import joint 3a (inflow port) and the cooling outport joint 3b (outlet) are pipe-connected to a cooling medium circulation system (not shown). The cooling medium is sent into the case body 1 from the cooling medium circulation system through the cooling import joint 3a. The cooling medium is sent from the case body 1 to the circulation system through the cooling outport joint 3b, or the case body 1 is sent from the cooling import joint 3a (inflow port) by opening and closing the valve using the fluid pressure of tap water or the like. The inside is fed and discharged from the cooling outport joint 3b (outlet).

The flow of the cooling medium in the case body 1 will be described with reference to FIGS. 8 and 9. In this embodiment, the flow path of the cooling medium is different between the second case 5 and the first case 4 constituting the case body 1. 8B and 9C show the flow path of the cooling medium of the second case 5. FIG. 9D shows the flow path of the cooling medium of the first case 4. As shown in FIG. 9B, the four side surfaces of the case body 1 provided with the cylinder 8 will be described as K-plane, L-plane, M-plane, and N-plane. 9C is a cross-sectional view taken along the arrow SS direction of FIG. 9A, and FIG. 9D is a cross-sectional view taken along the arrow RR direction of FIG. 9A. As shown in FIG. 10B, the first case 4 is provided with a first arc-shaped flow path 4b'(first connecting passage), and the second case 5 is provided with a second arc-shaped flow path 5b'(second connecting passage). Has been done.

In FIGS. 8B and 9C, the cooling medium flows into the second case 5 from the cooling import joint 3a provided on the N surface of the case body 1. In FIG. 9C, the cooling import joint 3a flows into the second arc-shaped flow path 5b'formed in an arc shape through the second case inflow path 5e1, and flows from the second arc-shaped flow path 5b'through the second case outflow path 5f1. It flows through the cooling flow path 8a of the cylinder 8 on the K surface and flows to the cooling flow path 8a on the side of the first case 4 (K surface cooling). As shown in FIG. 9D, the cooling medium flows from the cooling flow path 8a through the first case inflow passage 4g1 into the first arc-shaped flow path 4b'of the first case 4. Next, it flows from the first arc-shaped flow path 4b'through the first case outflow path 4h1 through the cooling flow path 8a of the cylinder on the L surface and flows to the cooling flow path 8a on the second case 5 side (L surface cooling).

In FIG. 9C, the cooling medium flows from the cooling flow path 8a through the second case inflow passage 5e2 into the second arc-shaped flow path 5b'of the second case 5. Next, it flows from the second arc-shaped flow path 5b'through the second case outflow path 5f2 through the cooling flow path 8a of the cylinder 8 on the M surface to the cooling flow path 8a on the first case 4 side (M surface cooling). As shown in FIG. 9D, the cooling medium flows from the cooling flow path 8a through the first case inflow passage 4g2 into the first arc-shaped flow path 4b'of the first case 4. Next, it flows from the first arc-shaped flow path 4b'from the first case outflow path 4h2 through the cooling flow path 8a of the cylinder on the M surface to the cooling flow path 8a on the second case 5 side (N-plane cooling).

In FIG. 9C, the cooling medium flows from the cooling flow path 8a through the second case inflow passage 5e3 into the second arc-shaped flow path 5b'of the second case 5. Then, it is discharged from the cooling outport joint 3b (outlet) from the second arc-shaped flow path 5b'through the second case outflow passage 5f3. The cooling medium may be cooled again by the circulation mechanism and returned to the case body 1, or when the cooling import joint 3a is connected to the water supply via a valve, the cooling outport joint 3b may be used. The spilled water may be drained.

The above flow of the cooling medium is shown by a thick arrow in the schematic diagram shown in FIG. 10B, and the first arc-shaped flow path 4b'(first connecting passage) of the first case 4 and the second arc-shaped flow path of the second case 5 are shown. 5b'(second connecting passage) is shown in a plan view. In this case, the cooling medium flowing through the case body 1 is the second case 5, the K-plane cylinder 8 (cooling flow path 8a), the L-plane cylinder 8 (cooling flow path 8a), and the M-plane to which the cooling import joint 3a is connected. A cylinder 8 (cooling flow path 8a), an N-side cylinder 8 (cooling flow path 8a), and a second case 5 to which a cooling outport joint 3b is connected flow in series on the outer periphery of a plurality of cylinders 8. As a result, the cooling flow paths 8a on the outer periphery of the plurality of cylinders 8 are connected in series via the first arc-shaped flow path 4b'or the second arc-shaped flow path 5b', and thus are connected to the first case 4 or the second case 5. Since the cooling medium flowing in from the provided inflow port always passes through the cooling flow paths 8a provided on the outer periphery of all the cylinders 8 before being discharged from the outflow port, the high-pressure fluid in the case body 1 is surely cooled. be able to. In this case, since the flow of the cooling medium is not affected by the installation posture of the case body 1, the degree of freedom in assembling the present device is improved.

Although the cooling import joint 3a and the cooling outport joint 3b were connected to the second case 5, they may be connected to the first case 4. Further, the cooling import joint 3a and the cooling outport joint 3b may be provided in different cases (first case 4 or second case 5), respectively.

Although the case where the rotary cylinder device is used as a compressor has been described, it can also be used as another fluid rotating machine such as a fluid pump or a vacuum drying device.

1 Case body 2a Air import joint 2b Air outport joint 3a Cooling import joint 3b Cooling outport joint 4 First case 4a, 5a, 10a Threaded hole 4b First annular flow path 4b'First arc-shaped flow path 4c First end surface cover 4d, 4i, 5d, 5i, 7a, 7b, 11, 17b, 17d Fixing screw 4e First case inflow path 4f, 4h1, 4h2 First case outflow path 4g1,4g2 First case inflow path 5th Two cases 5b Second annular flow path 5b'Second arc-shaped flow path 5c Second end face cover 5e1, 5e2, 5e3 Second case Inflow path 5f1, 5f2, 5f3 Second case Outflow path 6a First input / output shaft 6b Second entry Output shaft 8 Cylinder 8a Cooling flow path 8b, 8c Protruding part 8d Concave groove part 9 Cylinder head part 9e Concave groove 10 Head cover 12a, 12b, 12c, 12d, 12e, 12f, 12g, 12h O-ring 13a First annular flow path cover 13b Second annular flow path cover 14a, 14b First bearing 15a First balance weight 15b Second balance weight 16 First crank shaft P Piston unit 17a, 17c Pin 18 Eccentric cam 18a Cylinder hole 18b Cam part 19 First piston assembly 19a First piston body 19b First piston head part 19c, 20c Seal cup 19d, 20d Seal cup holding member 20 Second piston assembly 20a Second piston body 20b Second piston head part 21a, 21b Bearing holders 22a, 22b Second bearing 23a , 23b Third bearing 24a, 24b Second crank shaft 25 Virtual circle 26 Rolling circle 27 Rotating track 28 Guide shaft 29 First guide bearing 30 Second guide bearing 31 Cylinder chamber 32 Flow path cover 32a, 32b Protrusion 32c Inflow port 32d Outlet 32e Circumferential groove

The present invention, which is applied to some embodiments described below, comprises at least the following configurations. The rotation of the input / output shaft rotatably supported by the case body is converted into the reciprocating motion of a plurality of piston sets arranged orthogonally to the eccentric cam according to the principle of the inner cycle, and the fluid is supplied from the outside into the case body. This is a rotary cylinder device that sucks fluid into the cylinder chamber and discharges the compressed fluid from the cylinder chamber. Is provided with an annular flow path cover, respectively, to form a cooling flow path through which the cooling medium flows in an annular shape. The case body is formed by combining a first case and a second case, and is formed on the outer periphery of the plurality of cylinders. The cooling flow path provided in each, the first connecting flow path provided in the first case, and the second connecting flow path provided in the second case are connected in parallel, respectively, and the inflow port of the first case. The more taken-in cooling medium was guided to the second connecting flow path through the cooling flow path on the outer periphery of the plurality of cylinders connected in parallel via the first connecting flow path, and was provided in the second case. It is characterized by having a cooling structure discharged from the outlet.
According to the above configuration, the case body is provided with a cooling structure in which the cooling medium taken in from the inflow port passes through the cooling flow path provided on the outer periphery of at least one cylinder and is discharged from the outflow port. The cooling structure can be provided without increasing the installation area of the main body, and the cooling efficiency is also improved by passing the cooling medium around the outer circumference of the cylinder through the cooling flow path provided.
Further, the cooling medium that has flowed in from the inflow port of the first case flows in parallel from the first connecting flow path through the cooling flow paths on the outer circumferences of the plurality of cylinders and is discharged from the outflow port through the second connecting flow path. The flow path from when the medium flows into the case body to when it is discharged is short, and cooling can be performed efficiently. In this case, considering the flow of the cooling medium in the case body, it is preferable to arrange the first case downward and the second case upward in order to improve the cooling efficiency.

The rotation of the input / output shaft rotatably supported by the case body is converted into the reciprocating motion of a plurality of piston sets arranged orthogonally to the eccentric cam according to the principle of the inner cycle, and the fluid is supplied from the outside into the case body. A rotary cylinder device that sucks fluid into the cylinder chamber and discharges the compressed fluid from the cylinder chamber. An annular flow path cover is attached to the cylinder to form a cooling flow path through which the cooling medium flows in a ring shape. The case body is formed by combining the first case and the second case, and is provided in the first case. The cooling flow paths provided on the outer periphery of the plurality of cylinders are connected in series with each other via the first connecting flow path provided or the second connecting flow path provided in the second case. The cooling medium taken in from the inflow port provided in either the case or the second case passes through the cooling flow paths on the outer periphery of the plurality of cylinders connected in series for at least half a circumference, and the first case or the second case or the second case. It is characterized by having a cooling structure that is discharged from an outlet provided in any of the cases.
As a result, the cooling flow paths on the outer circumference of the cylinder assembled on the four side surfaces of the case body are connected in series via the first connecting flow path or the second connecting flow path, and thus are provided in the first case or the second case. The cooling medium that flows in from the inflow port always passes through the cooling passages provided on the outer circumference of all cylinders for at least half a circumference before being discharged from the outflow port, so that the high-pressure fluid inside the case body can be reliably cooled. can. In this case, the flow of the cooling medium is not affected by the installation posture of the case body, so that the degree of freedom in assembling the device is improved.

Claims (4)

The rotation of the input / output shaft rotatably supported by the case body is converted into the reciprocating motion of a plurality of piston sets arranged orthogonally to the eccentric cam according to the principle of the inner cycle, and the fluid is supplied from the outside into the case body. It is a rotary type cylinder device that sucks into the cylinder chamber and discharges the compressed fluid from the cylinder chamber.
An annular flow path cover is attached to the outer periphery of the plurality of cylinders assembled to the case body into which the plurality of piston sets are slidably inserted to form a cooling flow path through which the cooling medium flows in an annular shape. The case body is provided with a cooling structure in which a cooling medium taken in from the inflow port is passed through a cooling flow path provided on the outer periphery of at least one cylinder and discharged from the outflow port. Type cylinder device. The case body is composed of a combination of a first case and a second case, and the cooling structure includes a cooling flow path provided on the outer periphery of the plurality of cylinders and a first communication flow path provided in the first case. And the second connecting flow path provided in the second case are connected in parallel, and the cooling medium taken in from the inflow port of the first case is connected in parallel via the first connecting flow path. The rotary cylinder device according to claim 1, wherein the rotary cylinder device is guided to the second connecting flow path through the cooling flow path on the outer periphery of the plurality of cylinders and discharged from an outlet provided in the second case. The case body is composed of a combination of a first case and a second case, and the cooling structure includes a first connecting flow path provided in the first case or a second connecting flow path provided in the second case. The cooling channels provided on the outer periphery of the plurality of cylinders are connected in series to each other, and the cooling medium taken in from the inflow port provided in either the first case or the second case is provided. The rotary cylinder device according to claim 1, wherein the rotary cylinder device is discharged from an outlet provided in either the first case or the second case through the cooling flow path on the outer periphery of the plurality of cylinders connected in series. The rotary cylinder device according to any one of claims 1 to 3, wherein a heat radiating member is used for the cylinder cover that covers the cylinder head that closes the openings of the plurality of cylinders.

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