JPH04330383A - Variable stroke radial plunger device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention]

0001

[Field of Industrial Application] The present invention relates to devices such as radial plunger pumps and compressors, in which a cylinder and a plunger are arranged to extend in the radial direction around a main shaft. relates to a device of the type in which the reciprocating stroke of a plunger within a cylinder is variable.

0002

2. Description of the Related Art Such a variable stroke radial plunger device is known, for example, as disclosed in Japanese Patent Application No.
There is a proposal in No. 71637. An example of such a device will be briefly explained based on FIG. 12. This device has a main shaft (not shown) whose axis is C1,
A crank pin 501 having an axis C2 eccentric to the axis C1 is integrally formed on the main shaft. Therefore, when the main shaft is rotated, the crank pin 501 revolves around the axis C1. An eccentric collar 502 is attached to the crank pin 501 so as to be relatively rotatable. The outer peripheral surface 502a of this eccentric collar 502
The center C3 is eccentric with respect to the axis C2 of the crank pin 501.

The eccentric collar 502 is rotatable on the crank pin 501;
A stroke adjustment mechanism is attached to adjust the rotation angle of the eccentric collar 502 at the top, and the eccentric collar 502 is held at a predetermined rotation angle with respect to the crank pin 501, and these are adjusted according to the rotation of the main shaft. They revolve around the axis C1 as a unit. Note that when the rotation angle of the eccentric collar 502 is adjusted, the distance from the center C3 of the outer circumferential surface 502a of the eccentric collar 502 from the axis C1, that is, the outer circumferential surface 50
The radius of revolution of the center C3 of 2a with respect to the axis C1 can be adjusted.

A connecting ring 503 is mounted on the outer peripheral surface 502a of the eccentric collar 502 via a bearing 503a so as to be relatively rotatable. Plungers 505 are swingably attached to the connecting ring 503 via connecting pins 504 at equal intervals on the circumference, and
A single plunger 506 is formed integrally with this. Further, a cylinder casing 510 is arranged to be rotatable relative to the main shaft, and cylinders 5 are swingably mounted on the cylinder casing 510 at equal intervals on the circumference about the axis C1 by means of support pins 511.
08 is installed. Each cylinder 508 is formed with a cylinder hole that opens radially inward, and each plunger 505, 506 is inserted into this cylinder hole.

For this reason, for example, the cylinder casing 5
10 is held fixed and the main shaft is rotated to cause the crank pin 501 and eccentric collar 502 to revolve around the axis C1, the connecting ring 503 also rotates at the same period as the crank pin 501 and eccentric collar 502. The plungers 505 and 506 are connected to the cylinder 5.
It reciprocates within 08 and supplies and discharges working fluid (oil, air, etc.).

In this case, the discharge amount of the working fluid is proportional to the reciprocating stroke of the plungers 505 and 506 within the cylinder 508 if the rotation of the main shaft is constant. That is, by adjusting the reciprocating strokes of the plungers 505 and 506, the discharge amount can be variably adjusted. Therefore, as described above, this device is provided with a stroke adjustment mechanism that adjusts the rotation angle of the eccentric collar 502 with respect to the crank pin 501. The radius of revolution of the center C3 of the outer peripheral surface 502a of 502 with respect to the axis C1 can be adjusted. This outer peripheral surface 5
A connecting ring 503 is attached to 02a, and therefore, the stroke adjustment mechanism adjusts the revolution radius of the connecting ring 503 with respect to the axis C1 of the main shaft to adjust the reciprocating strokes of the plungers 505 and 506. Can be done.

[0007]

When the variable stroke radial plunger device is configured as described above, when the stroke of the plunger is adjusted by the stroke adjustment mechanism, the compression ratio also changes at the same time. This compression ratio change is a change in which the compression ratio is maximum when the stroke is maximum and the compression ratio is minimum when the stroke is minimum. The problem is that it does not necessarily meet the requirements of

This compression ratio change characteristic will be explained based on FIGS. 13 and 14. In FIG. 13, the rotation angle of the eccentric collar 502 is adjusted by the stroke adjustment mechanism,
The axis C1 of the main shaft, the axis C2 of the crank pin 501, and the center of the outer peripheral surface 502a of the eccentric collar 502 (
In other words, the center C3 of the connecting ring 503 is arranged in a straight line in this order, and at this time, the radius of revolution of the center C3 of the connecting ring 503 is maximum, and the reciprocating stroke S of the plunger 505 is maximum. becomes.

In the state shown in FIG. 13(A), the plunger 50
5 is located at the top dead center, and from this state the crank pin 501
When the eccentric collar 502 rotates 180 degrees around the axis C1 as a unit, the plunger 505 is located at the bottom dead center in the state shown in FIG. 13(B). The reciprocating stroke of the plunger 505 from the top dead center to the bottom dead center at this time is S1. The compression ratio RC1 in this case is
When the top clearance (distance between the upper end of the plunger 505 and the upper end surface of the cylinder hole in the cylinder 508) when the plunger 505 is located at the top dead center is D1, RC1=(S1+D1)/D1=S1/D1+1. .

Next, from this state, the rotation angle of the eccentric collar 502 is adjusted by the stroke adjustment mechanism, and the axis C1 of the main shaft, the axis C2 of the crank pin 501, and the center C3 of the connecting ring 503 are aligned. 14(A). As a result, the center C of the connecting ring 503
The radius of revolution of the main shaft No. 3 relative to the axis C1 decreases, and the reciprocating stroke S of the plunger 505 also decreases.

In this case, the plunger 505 is located at the top dead center in the state shown in FIG. Then, the state shown in FIG. 14(B) is reached, and the plunger 505 is located at the bottom dead center. The reciprocating stroke of the plunger 505 from the top dead center to the bottom dead center at this time is S2, which is smaller than the stroke S1 in the case of FIG. 13 above. At the same time, as shown,
The top clearance when the plunger 505 is located at the top dead center is D2
This becomes larger than the top gap D1 in the case of FIG. 13 above. The compression ratio RC2 at this time is RC2=(S2+D2)/D2=S2/D2+1.

[0012] Here, S1>S2 and D1<D2
Therefore, RC1>RC2. That is, in the variable stroke radial plunger device described above, as shown in FIG. 15, the compression ratio RC is maximum when the stroke of the plunger is maximum and the discharge amount is maximum, and as the stroke is made smaller to reduce the discharge amount. The compression ratio RC becomes smaller. In general, the working fluid is compressible (
For example, air, etc.), the larger (that is, the higher) the compression ratio RC, the higher the operating efficiency of the device. Therefore, in the case of the conventional variable stroke radial plunger device as described above, the efficiency is maximum when the discharge amount is maximum, but there is a problem in that the efficiency decreases as the discharge amount is decreased.

Furthermore, when the variable stroke radial plunger device is used as an air compressor, for example, when the reservoir tank is nearly empty, such as at the start of operation, a large amount of air is pumped into the tank even if the pressure is low. It is preferable to supply even a small amount of high-pressure air when air accumulates in the tank and the internal pressure rises. However, in the case of the variable stroke radial plunger device, the compression ratio is maximum when the discharge amount is maximum, but as the stroke of the plunger is made smaller to reduce the discharge amount, the compression ratio becomes smaller. There is a problem in that as the discharge amount decreases, it becomes difficult to supply high pressure air.

The present invention has been made in view of the above-mentioned problems, and provides a variable stroke radial plunger device configured to provide preferable compression ratio change characteristics in response to adjustment of the discharge amount by adjusting the stroke of the plunger. The purpose is to provide.

[0015]

[Means for Solving the Problems] In order to achieve the above object, a variable stroke radial plunger device according to the present invention has the following features:
It has a main shaft that is rotatable relative to the casing and has a crank pin that is eccentric from the relative rotation axis, and an eccentric collar that has an outer peripheral surface that is eccentric with respect to the crank pin is attached to the crank pin, and the outer periphery of the eccentric collar is attached to the crank pin. A connecting ring is rotatably mounted on the surface, the inner end of the plunger is pivoted to the connecting ring, and the plunger is inserted into the cylinder hole of the cylinder that is swingably attached to the casing. It is comprised of a stroke adjustment mechanism that adjusts the rotation angle of the eccentric collar above, and a double mechanism that positions the connecting ring relative to the main shaft and casing.

[0016] This double mechanism includes a first internal gear which is disposed concentrically with the main shaft and connected to the casing, and a first internal gear which is disposed on the main shaft so as to be rotatable about the axis of the crank pin. and a second internal gear that meshes with the external gear and rotates concentrically and integrally with the connecting ring. The number of teeth of the two internal gears is the same, and the number of teeth of the external gear is smaller than the number of teeth of the first and second internal gears.

Note that when the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so that the reciprocating stroke of the plunger within the cylinder hole is maximized, the pivot axis of the plunger inserted into this cylinder to the connecting ring Reference plane A connecting the center axis of revolution and the center axis of the main shaft
In contrast, the center of swing of the cylinder relative to the casing is
The positional relationship of each member constituting the double mechanism is set so that the members deviate from each other by a predetermined installation deviation angle θ in the circumferential direction about the central axis of the main shaft.

In this case, when the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so as to reduce the reciprocating stroke of the plunger within the cylinder hole from the maximum state, the pivot of the plunger to the connecting ring is When the shaft revolves in response to the rotation of the main shaft, the pivot axis D, which connects the center axis of revolution and the center axis of the main shaft, is separated from the reference plane A, and the center of rotation of the cylinder and the center of the main shaft are separated from each other. It is preferable to configure the double mechanism so as to move in the direction of the cylinder swing axis center plane C that connects the cylinder to the shaft. Furthermore, as the reciprocating stroke of the plunger becomes smaller, the compression ratio changes due to the adjustment of the reciprocating stroke of the plunger by the stroke adjustment mechanism and the movement adjustment of the pivot axis surface D by the double mechanism accompanying this adjustment. It may be set to be used within a reciprocating stroke adjustment range in which the reciprocating stroke becomes large.

[0019]In place of the double mechanism, a first external gear is arranged concentrically with the main shaft and connected to the casing, and a first external gear is arranged on the main shaft so as to be rotatable about the axis of the crank pin. The second external gear is arranged to mesh with the internal gear and rotate integrally concentrically with the connecting ring. Alternatively, a double mechanism may be used in which the second external gear has the same number of teeth and the internal gear has more teeth than the first and second internal gears.

Furthermore, the first sprocket is disposed concentrically with the main shaft and connected to the casing, and the first sprocket is disposed on the main shaft so as to be rotatable about the axis of the crank pin. a second sprocket with a different number of teeth;
A first chain spanned between the sprockets, a third sprocket having the same number of teeth as the second sprocket and arranged to rotate together concentrically with the second sprocket, and a third sprocket arranged to rotate together concentrically with the connecting ring. A double mechanism may be used, which includes a fourth sprocket having the same number of teeth as the first sprocket, and a second chain spanning between the third and fourth sprockets.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. 1 and 2 show a variable stroke radial plunger type compressor as an embodiment of the present invention. This compressor consists of a two-part casing 1 connected by bolts 8 as shown in the figure.
, 2, and a main shaft 11 (consisting of 11a, 11b) is rotatably supported by bearings 5a, 5b at the center of the casings 1, 2. Note that a lid member 3 for forming a discharge passage 41 is coupled to the right side surface of the right casing 2.

The main shaft 11 has a left main shaft half 11a that protrudes outward for external drive, and an axis C2 that is eccentric by a predetermined distance L1 with respect to the axis (rotation center) C1 of the main shaft 11. crank pin 12 with
and a right main shaft half 11b integrally formed, and the two halves 11a and 11b are connected by fitting the tip of the crank pin 12 into the eccentric hole of the left main shaft half 11a. . Therefore, the main shaft 11 and the crank pin 12 rotate together around the axis C1, and the axis C2 of the crank pin 12 rotates around the axis C1.
revolve around.

An eccentric collar 13 is attached to the crank pin 12 so as to be rotatable relative thereto. The outer peripheral surface 13a of this eccentric collar 13 is cylindrical, and its center axis C3 is a predetermined distance L2 from the axis C2 of the crank pin 12.
Only eccentric. A connecting ring 14 is rotatably attached to the outer peripheral surface 13a of the eccentric collar 13. Therefore, the connecting ring 14 has a central axis C of the outer circumferential surface 13a.
3 on the eccentric collar 13.

As shown in FIG. 2, five cylinders 18 are arranged radially around the connecting ring 14. As shown in FIG. Each of these cylinders 18 has a pair of left and right trunnions 18b, and each cylinder 18 is swingably attached to the casings 1 and 2 at the trunnions 18b. The centers of the trunnions 18b of the five cylinders 18, that is, the swing centers of the cylinders 18, are located at equal intervals on the same radius around the axis C1 of the main shaft 11. Cylinder hole 1 of each cylinder 18
8a opens on the inner diameter side, and each cylinder hole 18a
Five plungers 16 are slidably inserted therein from the inner diameter side. Each of the plungers 16 has an inner diameter end portion pivotally supported by a pin 15 on the connecting ring 14 .

Plunger 16 in cylinder hole 18a
The internal space (cylinder chamber) surrounded by the trunnion 18b passes through a check valve 40 disposed in a through hole formed in the right trunnion 18b, and a discharge passage 41 formed between the casing 2 and the lid member 3. communicate with. check valve 40
is a discharge passage 41 for discharging fluid (for example, air) in the cylinder chamber.
, but prevent fluid from flowing in the opposite direction. On the other hand, the tip of each plunger 16 has openings 16a, 16.
a is formed, and a reed valve 17 is attached to cover the openings 16a, 16a from the outside. The reed valve 17 is a flexible member. Therefore, the fluid in the internal space 6 of the casings 1 and 2 pushes up the reed valve 17 and flows into the cylinder chamber, but the flow in the opposite direction is caused by the reed valve 17. It is now blocked by.

Therefore, as will be described later, the plunger 16 is moved into the cylinder hole 1 by the rotational drive of the main shaft 11.
When reciprocating within 8a, while the plunger 16 moves from the top dead center to the bottom dead center, the fluid in the internal space 6 of the casings 1 and 2 flows into the cylinder chamber through the reed valve 17, and the plunger 16 The fluid flowing into the cylinder chamber while the cylinder moves from the bottom dead center to the top dead center flows into the check valve 4.
0 and is discharged into the discharge passage 41, and operates as a compressor.

The compressor of this example is provided with a stroke adjustment mechanism for variably adjusting its discharge capacity and a double mechanism for ensuring the above operation. These will be explained below.

The stroke adjustment mechanism includes an internal gear 13b that is integrally formed on the right side of the eccentric collar 13 and concentric with the axis C2 of the crank pin 12, and a right main shaft half that constitutes the main shaft 11. A rotating sleeve 21 and a sliding sleeve 22 are disposed on the body 11b to be rotatable about the axis C1 of the main shaft 11.
Consists of etc. An external gear 21a that meshes with the internal gear 13b is formed at the left end of the rotating sleeve 21, and the rotating sleeve 21 is connected to the right main shaft half 11b.
By rotating the eccentric collar 13 on the crank pin 12, the eccentric collar 13 can be rotated on the crank pin 12.

An internal spline 21b is formed on the inner diameter of the rotating sleeve 21.
b meshes with an external spline 22a formed on the outer diameter of the sliding sleeve 22. Furthermore, the sliding sleeve 22
An internal spline 22b is also formed on the inner diameter part of the
This internal spline 22b is connected to the right main shaft half 11.
It meshes with the external spline 11c formed at b. A shifter receiving member 24 is mounted on the sliding sleeve 22 via a bearing 23, and this shifter receiving member 24 is locked to the tip of a shifter lever 25. The shifter lever 25 can be rotated about a support shaft 26, and the rotation of the shifter lever 25 causes the sliding sleeve 22 to slide left and right via the shifter receiving member 24. Here, the internal spline 21b of the rotating sleeve 21 and the external spline 22a of the sliding sleeve 22 are
At least one of the internal spline 22b of the sliding sleeve 22 and the external spline 11c of the right main shaft half 11b is a helical spline. Therefore, when the sliding sleeve 22 is slid left and right as described above, the rotating sleeve 21 is rotated, and the eccentric collar 13 is rotated on the crank pin 12.

By rotating the eccentric collar 13, the reciprocating stroke S of the plunger 16 is adjusted. This will be explained using FIG. 3. The axis C1 of the main shaft 11, the axis C2 of the crank pin 12, and the center of the outer peripheral surface 13a of the eccentric collar 13 (the center of the connecting ring 14)
From the state where C3 is lined up in a straight line facing the direction of arrow P,
Consider the case where the eccentric collar 13 is rotated. Note that the amount of eccentricity of the axis C2 with respect to the axis C1 is L1, and the amount of eccentricity of the center C3 with respect to the axis C2 is L2, and at this time, the center C3 is eccentrically positioned by a distance L3 with respect to the axis C1. When the main shaft 11 is rotated with the axes C1, C2, and C3 aligned in a straight line as described above, the vertical movement of the outer peripheral surface 13a of the eccentric collar 13 in the direction of arrow P is the eccentric distance of the center C3. The value becomes 2L3, which is twice L3. Therefore, the connecting ring 14 also moves up and down by a distance 2L3, and the reciprocating stroke S of the plunger 16 is determined accordingly.

Consider the case where the eccentric collar 13 is rotated as shown by the two-dot chain line in the figure from the above state. In this case, in order to keep the center C3 of the outer peripheral surface 13a of the eccentric collar 13 pointing in the direction of the arrow P, the main shaft 11 is rotated 45 degrees counterclockwise, and the eccentric collar 13 is rotated clockwise on the crank pin 12. It's rotated 90 degrees. As a result, the crank pin 12 moves to the position indicated by 12', and its axis C2 moves to the position C2'. At the same time, the outer peripheral surface 13a of the eccentric collar 13 also moves to the position indicated by 13a', and its center C3 moves to the position C3'. As a result, the eccentric distance of the center C3' of the outer peripheral surface 13a of the eccentric collar 13 with respect to the axis C1 of the main shaft 11 is L3' (
<L3). Therefore, when the main shaft 11 is rotated in this state, the outer peripheral surface 13a of the eccentric collar 13'
The vertical movement of ' in the direction of arrow P is the eccentric distance L of center C3'.
The value becomes 2L3' which is twice 3'. For this reason, connecting ring 1
4 also becomes small to 2L3', and the reciprocating stroke S of the plunger 16 also becomes small correspondingly.

After adjusting the stroke of the plunger 16 as described above, in order to cause the plunger 16 to reciprocate when the eccentric collar 13 is rotated integrally with the rotation of the main shaft 11, the connection ring is 14 needs to revolve around the main shaft 11 without rotating. In order to obtain such movement of the connecting ring 14, a double mechanism is provided in this example.

This double mechanism includes a first internal gear 31 connected to the casing 1 concentrically with the axis C1 of the main shaft 11, and a first internal gear 31 connected to the casing 1 concentrically with the axis C1 of the crank pin 12, and a first internal gear 31 connected to the left main shaft half 11a concentrically with the axis C2 of the crank pin 12. The axis C of the rotatably attached external gear 32 and the outer peripheral surface 13a of the eccentric collar 13
3 (which is also the axis of the connecting ring 14) and a second internal gear 33 that is concentric with the connecting ring 14 and integrally formed with the connecting ring 14. Number of teeth Z1 of first internal gear 31 and second internal gear 33
The number of teeth Z3 of the external gear 32 is equal, and the number of teeth Z2 of the external gear 32 is smaller than the number of teeth Z1 and Z3 of both the internal gears 31 and 33. and,
The first internal gear 31 and the external gear 32 mesh with each other, and the external gear 3
2 and the second internal gear 33 are in mesh with each other.

The operation of this double mechanism will be explained using FIG. 4. In the compressor of this example, the main shaft 11 is rotationally driven. Since the eccentric collar 13 is connected to the main shaft 11 by a stroke adjustment mechanism, the axial center of the crank pin 12, that is, the axial center C2 of the external gear 32, and the eccentric collar 13 are adjusted according to the rotation of the main shaft 11. The axis C3 of the outer circumferential surface 13a, that is, the axis C3 of the second internal gear 33, is the axis C3 of the machine shaft 11.
It revolves around 1. For example, the main shaft 11 is
As illustrated, when rotated by angle β1, axes C2 and C3 revolve around axis C1 by angle β1. Here, since the first internal gear 31 is coupled and fixed to the casing 1, the axis C2 of the external gear 32 is at an angle β1
When the external gear 32 revolves by an angle β2, the external gear 32 rotates in the opposite direction by an angle β2. Since the number of teeth and rotation angle of both gears 31 and 32 are inversely proportional, β2=-Z1/Z2×β1
...The relationship is (1).

When the external gear 32 is rotated by an angle β2, the rotation angle β3 of the second internal gear 33 is calculated as β3=Z2/Z3×β2=−Z1/Z3×β1 using equation (1).・・・
・(2) becomes. The first internal gear 31 of the second internal gear 33
The rotation angle (absolute rotation angle) β4 for the axis C2 is the sum of the revolution angle β1 of the axis C2 and the rotation angle β3, so β4=β1+β3=(Z3-Z1)/Z3×
β1...(3). Here, as can be seen from equation (3), the first internal gear 31 and the second internal gear 33
Since the number of teeth Z1 and Z3 are equal, the rotation angle β4 of the second internal gear 33 is zero, and the second internal gear 33 does not rotate.

As can be seen from the above, in this compressor, if the main shaft 11 is driven to rotate with respect to the fixed casings 1 and 2, the above-mentioned double mechanism will rotate the connecting ring in accordance with the rotation of the main shaft 11. 14
It operates as a mechanism that rotates around the planet without rotating it.

Since the connecting ring 14 is rotatably disposed on the outer circumferential surface 13a of the eccentric collar 13, the revolution movement of the connecting ring 14 in response to the rotation of the main shaft 11 is centered around the outer circumferential surface 13a of the eccentric collar 13. This is the same as the revolution movement of the axis C3, and is the movement shown by the rotation locus F1 in FIG. Similarly, as shown in FIG.
The pivot shaft C4 of each plunger 16 (pivot supported by the connecting pin 15) also performs the same revolution movement as the connection ring 14, and the movement is shown by a rotation locus F2 whose revolution center is C6. As a result, the plunger 16 is connected to the casings 1 and 2.
Each reciprocates within a cylinder 18 which is swingably connected to the cylinder 18.

In the compressor of this example, as shown in FIG. When the rotation angle of the eccentric collar 13 is adjusted so that C2 and the center C3 of the outer peripheral surface 13a of the eccentric collar 13 are aligned in a straight line as shown in the figure, the plunger 16 at this time is adjusted.
The swing axis C5 of the cylinder 18 and the axis C of the main shaft 11 with respect to the reference line (plane) A connecting the center C6 of the revolution of the pivot axis C4 and the axis C1 of the main shaft 11.
Cylinder 1 so that the direction of the cylinder swing axis center line (plane) C that connects Cylinder 1 with
8, the swing axis C5 is positioned. Note that this predetermined angle θ is referred to as a mounting deviation angle.

From this state, when the stroke adjustment mechanism adjusts the rotation angle of the eccentric collar 13 to adjust the stroke, the connecting ring 14 is rotated and the revolution of the pivot axis C4 of the plunger 16 is adjusted. The center C6 moves in a direction away from the reference plane A and closer to the cylinder swing axis center plane C. That is, when this stroke adjustment is performed, the double mechanism operates so that the pivot axis plane D connecting the center C6 of the revolution movement of the pivot axis C4 of the plunger 16 and the axis C1 of the main shaft 11 becomes the plane A. Move away from and approach surface C. As can be seen from this, the reference plane A is a fixed plane connecting the center C6 of the revolution of the pivot axis C4 of the plunger 16 and the axis C1 of the main shaft 11 at the maximum stroke. The pivot axis surface D is a surface that moves by the operation of a double mechanism in accordance with stroke adjustment. Naturally, at the maximum stroke, the reference plane A and the pivot axis plane D overlap. Here, the angle formed by the pivot axis plane D with respect to the reference plane A is referred to as a movement angle δ. This movement angle δ corresponds to the rotation angle of the connecting ring 14, and changes to become larger in accordance with the stroke adjustment.

This will be explained based on FIG. 6. Rotate the shifter lever 25 from a state where the axes C1, C2, and C3 are aligned to give the maximum stroke to the plunger 16, and move the eccentric collar 13 to the crank pin 12.
Consider the case where the rotation is made by an angle of 2γ1 relative to the rotation angle. As a result, the axis C3 rotates by an angle 2γ1 with respect to the axis C2. At this time, if the axis C2 is rotated by an angle γ1 in the opposite direction around the axis C1, as shown in the figure, The shaft center C3 moves to C3'' while maintaining the same phase, and the eccentricity of the connecting ring 14 that gives a predetermined stroke to the plunger 16 changes from L3 to L3'. be.

At this time, the rotation angle, ie, the movement angle δ, of the second internal gear 33, ie, the coupling ring 14, is determined. First, while meshing with the first internal gear 31 coupled to the casings 1 and 2, the axis C2 of the external gear 32 is aligned with C2'
Consider the movement of the meshing point Q of both gears 31 and 32 when the gears 31 and 32 move by an angle γ1. At this time, the external gear 32
The axis C2 of moves to the point shown as C2' in the figure, and the engagement point Q moves to Q1. External gear 3 at this time
The rolling angle γ2 of 2 is at the point Q' corresponding to the original meshing point.
This is an angle corresponding to the arc length between the meshing point Q1 and the meshing point Q1. Here, since this arc length Q'Q1 is equal to the arc length QQ1, Z
The relationship 1×γ1=Z2×γ2 is established, and γ2=
Z1/Z2×γ1...(4
). At this time, the axis C3 moves to C3', and the position of the meshing point P between the external gear 32 and the second internal gear 33 continues to move to P'.

Next, the second internal gear 33 is rolled around the axis C2', and its axis C3' is moved to C3''. This completes the work of shortening the inter-axle distance L3 to L3'. As a result, the meshing point P' between the external gear 32 and the second internal gear 33 rolls and moves to the point P1.
′ moves to P″. In this way, the first meshing point P on the second internal gear 33 with the external gear 32 eventually moves to P″, so the point corresponding to the second internal gear 33 moves to P″. gear gear 3
The phase change angle of No. 3 is represented by the angle δ from point P to point P'' centering on the axis C3''. At this time, the external gear 32
The rolling distance of the second internal gear 33, that is, the arc P′P1 is equal to the rolling distance of the second internal gear 33, that is, the arc P″P1. The rolling angle of the external gear 32 is γ3 (=2γ1−γ2), Since the rolling angle of the internal gear 33 is (γ1-δ), Z2(2γ1-γ2)=Z3(γ1-δ)...(
5) The following relationship holds true.

In this equation (5), equation (4) and Z1=Z
Substituting the relational expression 3, δ=(Z1-Z2)/Z1×2γ1...
The relational expression (6) is obtained. Equation (6) shows the relationship between the rotation angle (phase change angle) δ of the second internal gear 33 and the rotation angle (=2γ1) of the eccentric collar 13 for stroke adjustment. Here, the rotation angle δ of the second internal gear 33 is the rotation angle, that is, the movement angle of the connecting ring 14, and this (6
) As can be seen from the equation, when the eccentric collar 13 is rotated to adjust the stroke, the connecting ring 14 rotates, and the center C6 of the revolution of the pivot axis C4 of the plunger 16 moves.

Here, the first and second internal gears 31, 3
3, the number of teeth of the external gear 32 is set to Z1 = Z3 = 49, the number of teeth of the external gear 32 is set to Z2 = 40, and the eccentricity of each axis C2, C3 is set to L1 = L2 = 4.5 mm. The relationship between the rotation angles γ1 and δ and the eccentricity L3 (this is referred to as a stroke radius) of the shaft center C3 is as shown in Table 1 below.

[0045]

[Table 1]

The rotation angle γ1 is the rotation angle of the axis C2 with respect to the axis C1, and the rotation angle of the eccentric collar 13 on the crank pin 12 at this time is 2γ1. For this reason,
When the rotation angle γ1 = 0°, the stroke radius L3 is maximum (
9.0 mm), and when the rotation angle γ1 = 90°,
The rotation angle of the eccentric collar 13 is 180°, the axis C3 overlaps the axis C1, and the stroke radius L3 is the minimum (0 mm
). As shown in Table 1 above, the eccentric collar 13 is set to 0.
When the stroke radius L3 is changed from the maximum to the minimum by rotating from 180 degrees, the connecting ring 14 will move 32.4 degrees.
As it rotates, the angle formed by the pivot axis plane D with respect to the reference plane A, that is, the movement angle δ also changes from 0° to 32.4°.

In this example, when the stroke radius L3 is maximum, the movement angle δ is the minimum (=0°), and as the stroke radius L3 becomes smaller, the movement angle δ increases, and the stroke radius L3 becomes smaller. Since the movement angle δ is set to be maximum when it is minimum, the angle formed by the cylinder swing axis center surface C with respect to the reference surface A, that is, the mounting deviation angle θ=
The center axis C of the cylinder 18 swings so that the angle is 32.4°.
5 is positioned. Further, when the stroke radius L3 is the minimum, the movement angle δ=32.4°, and at this time, the pivot axis D overlaps the cylinder swing axis C.

As mentioned above, the movement angle δ changes according to the stroke adjustment, but here, without a double mechanism and with the stroke constant, the pivot axis surface D is moved to the position at the maximum stroke. Let us consider the difference in the compression ratio RC between the case where the cylinder is placed at the position (overlapping with the reference plane A) and the case where it is placed at the position at the minimum stroke (position where it overlaps with the cylinder swing axis center plane C). Figure 7(A) shows the case where the pivot axis surface D is placed at the position at the maximum stroke (a position overlapping the reference plane A), and Figure 7(B) shows the case where the pivot axis center surface D is placed at the position at the minimum stroke. The case where the cylinder is placed at a position (a position overlapping with the cylinder swing axis center plane C) is shown.

In the case of FIG. 7(A), the main shaft 1
Since the axis C1 of the plunger 1 and the revolution center C6 of the pivot axis C4 of the plunger 16 to the connecting ring 14 are aligned on the reference plane A, the top gap d1 at this time becomes the maximum as shown in the figure. However, in the case of FIG. 7(B), the axis C1 of the main shaft 11 and the revolution center C6 of the pivot axis C4 of the plunger 16 to the connecting ring 14 overlap with the cylinder swing axis plane C, and the pivot The spindle center plane D moves in the circumferential direction by 32.4° with respect to the reference plane A. Here, since the distance from the axis C1 of the main shaft 11 to the swing axis C5 of the cylinder 18 does not change, and the length of the plunger 16 also does not change, in this case, in the case of FIG. 7(A) In comparison, the top gap is reduced to d2 (>d1) as shown in the figure. For this reason,
In this case, the stroke does not change, but the compression ratio RC is minimum in FIG. 7(A) and maximum in FIG. 7(B).

In the above description, the change in the compression ratio RC was explained when the position of the pivot axis D was changed while the stroke radius L3 remained constant. However, in reality, the positional change of the pivot axis D is caused by the action of a double mechanism when the stroke is adjusted by changing the rotation angle of the eccentric collar 13, and the stroke radius L3 is constant. This is not going to change.

For this reason, based on FIG. 9, a description will be given of changes in the position of each axis, etc. with respect to changes in the rotation angle γ1 of the axis C2 with respect to the axis C1 shown in Table 1. In this example, as described above, when the stroke adjustment mechanism adjusts the stroke of the plunger 16 to the maximum, the movement angle δ becomes 0° (minimum), and the stroke adjustment mechanism adjusts the stroke of the plunger 16 to the minimum. The movement angle δ is set to be 32.4° (maximum) when adjusted so that the movement angle δ becomes 32.4° (maximum).

First, when the stroke of the plunger 16 is adjusted to the maximum by the stroke adjustment mechanism, the axis C3 of the outer circumferential surface 13a of the eccentric collar 13 is farthest from the axis C1 of the main shaft 11, as shown in Table 1. As shown in , the stroke radius L3 is maximum at 9.0 mm, and when the main shaft 11 is rotated, the axis C3 revolves on the orbit F1. Therefore, the revolution radius of the pivot axis C4 of the plunger 16 to the connecting ring 14 is also the same as the stroke radius L3, which is the maximum, and the plunger 16 revolves on the revolution locus F2. Note that the central axis of this orbit F2 is C6,
The plane connecting this central axis C6 and the central axis C1 of the main shaft 11 at this time is the reference plane A. Then, the cylinder 18 is attached to the casings 1 and 2 with the swing center axis C5 of the cylinder 18 being located at a position shifted in the rotational direction by the mounting deviation angle θ (=32.4°) with respect to this reference plane A. ing.

As mentioned above, the pivot axis C4 is on the orbit F2.
If it moves above, the plunger 16 reciprocates within the cylinder 18, but the line B connecting the center axis C6 of the orbit F2 and the swing center axis C5 of the cylinder 18 and the orbit F2
2, the plunger 16 reaches the top dead center, and at another intersection BDC, the plunger 16 reaches the bottom dead center. Therefore, the reciprocating stroke of the plunger 16 within the cylinder 18 is twice the revolution radius (=stroke radius L3).

Next, when the eccentric collar 13 is rotated by 90° using the stroke adjustment mechanism, that is, the rotation angle γ=4.
Assuming 5°, as shown in Table 1, the movement angle δ1=16
．． 2°, the central axis of the outer circumferential surface 13a of the eccentric collar 13 moves to the position indicated by C3', and the stroke radius L3=6.
．． 4mm, which is smaller than the maximum stroke mentioned above. To explain this with reference to FIG. 9, the above rotation causes the connecting ring 1 to
4 is rotated clockwise, and the pivot axis of the plunger 16 moves to the position indicated by C4'. Therefore, when the main shaft 11 is rotated, the axis C3' changes to the orbit F1'
The pivot axis C4' of the plunger 16 revolves on a revolution locus F2'. The center axis of this orbit F2' is C6', and this center axis C6' and the main shaft 11
The moving angle δ1 of the pivot axis center plane D' connecting the center axis C1 of the pivot axis C1 with respect to the reference plane A is δ1=16.2°.

After that, when the eccentric collar 13 is further rotated by 90 degrees using the stroke adjustment mechanism, that is, when the rotation angle γ is set to 90 degrees, the movement angle δ becomes as shown in Table 1.
2=32.4°, and the outer peripheral surface 13a of the eccentric collar 13
The central axis of overlaps with the central axis C1 of the main shaft 11,
The stroke radius L3 is the minimum of 0 mm. This rotation causes the connecting ring 14 to further rotate clockwise, and the pivot axis of the plunger 16 moves to the position indicated by C4''. Since the stroke radius L3 = 0 mm, the main shaft 11 Even when rotated, the pivot axis C4'' of the plunger 16 remains in the same position, and the revolution center axis C4'' remains in the same position.
6'' coincides with the pivot axis C4'' of the plunger 16, and the moving angle δ2=32.4°.

As mentioned above, in the case of the compressor of this example, the movement angle δ is the minimum at the maximum stroke, and the movement angle δ is the maximum at the minimum stroke.
3 and 14, and the compression ratio change characteristic due to a change in the position of the pivot axis surface D explained with reference to FIG. Settings can be made. In the case of this example, this change is as shown in FIG. 8, for example.

Therefore, for example, if this compressor is used within the area indicated by M in FIG.
It is possible to obtain a change characteristic in which the compression ratio is small at the maximum stroke within this region M and becomes large at the minimum stroke. When this compressor is used as an air compressor, it has the following advantages. First, when the reservoir tank is empty when the compressor starts operating, it is desirable to supply a large amount of air even if the pressure is low; in this case, the plunger stroke is maximized to supply a large amount of air. . After this, as air gradually accumulates in the reservoir tank and the internal pressure rises, it will no longer be necessary to supply that much air.
If the pressure is not high, air cannot be supplied into the tank. For this reason, control is performed to gradually reduce the stroke of the plunger and increase the compression ratio as the tank internal pressure increases.

Note that the compression ratio change characteristics corresponding to the stroke adjustment differ depending on the dimensions of each component and the configurations of the stroke adjustment mechanism and the double mechanism. Therefore, for example, it is possible to set the compression ratio to be a substantially constant value over a predetermined stroke range. If such a compression ratio change characteristic is set, the compressor can be operated with the compression ratio always set at a high value within a predetermined stroke range, and the compressor can be operated with high efficiency at all times. In addition, in the above example, when the plunger reaches its minimum stroke, the movement angle δ is 32.4°.
An example is shown in which the pivot axis plane D is set to overlap the cylinder swing axis plane C, and the movement angle δ at this time is
It goes without saying that the installation deviation angle θ can also be set to an arbitrary angle.

In the above description, an example has been described in which the double mechanism is composed of the first and second internal gears 31 and 33 and one external gear 32. However, the double mechanism is not limited to this type of mechanism; instead, a first external gear having external teeth concentric with the axis C1 of the main shaft 11 and coupled to the casings 1 and 2 may be used. The main shaft 1 has internal teeth concentric with the axis C2 of the crank pin 12.
1, and external teeth concentric with the axis C3 of the outer peripheral surface 13a of the eccentric collar 13.
The second external gear may be formed integrally with the connecting ring 13. In this double mechanism, the first and second external gears have the same number of teeth, and the internal gear has the same number of teeth.
and more than the number of teeth of the second external gear. Then, the first external gear and the internal gear mesh, and the second internal gear also meshes with the first external gear.
It also meshes with external gears. The operation of the double mechanism in this case is the same as the operation of the double mechanism described above, so a description thereof will be omitted.

[0060] Furthermore, although an example in which a double mechanism is constructed by a combination of gears has been described above, a double mechanism may also be constructed by a chain and a sprocket, as shown in FIGS. 10 and 11. FIG. 10 (and FIG. 11) shows a first sprocket 51 (51') connected to the casings 1 and 2 and arranged on the main shaft C1, and a first sprocket 51 (51') arranged rotatably on the auxiliary shaft C2. 2 sprocket 52
(52'), a first chain 55 (55') wound between both sprockets 51 and 52, and a third sprocket 53 (53') connected to and attached to the second sprocket 52.
53'), a fourth sprocket 54 (54') rotatably disposed on the sub-shaft C3, and both sprockets 53, 5
A double mechanism 50 (50') comprising a second chain 56 (56') wound between two chains is shown.

In the case of this double mechanism 50 (50'), the distance between the main shaft C1 and the auxiliary shaft C2 and the auxiliary shaft C2
and the auxiliary axis C3 while keeping the distance between the auxiliary axis C2 and the auxiliary axis C3 constant.
By changing the position of , it is possible to variably adjust the distance (stroke radius) between the main shaft C1 and the sub-shaft C3. Note that the first and fourth sprockets 51 (51'), 5
4 (54') have the same number of teeth, and the second and third sprockets 52 (52') and 53 (53') have the same number of teeth. However, the first and fourth sprockets 51 in FIG.
, 54 teeth are the second and third sprockets 52, 53
The number of teeth of the first and fourth sprockets 51' and 54' in FIG.
It is less than the number of teeth 2' and 53'.

[0062]

[Effects of the Invention] As explained above, according to the present invention,
The main shaft has a crank pin that is eccentric from its rotation axis, and an eccentric collar having an outer peripheral surface that is eccentric with respect to the crank pin is mounted on the crank pin, and a connecting ring is rotatably mounted on the outer peripheral surface of the eccentric collar. The inner end of the plunger is pivotally supported by a connecting ring, and the plunger is inserted into the cylinder hole of a cylinder that is swingably attached to the casing. A variable stroke radial plunger device includes a stroke adjustment mechanism for adjusting the stroke, and a double mechanism for positioning the connecting ring with respect to the main shaft and the casing, and the double mechanism is concentrically coupled to the casing and arranged. a first internal gear provided on the main shaft; an external gear disposed on the main shaft so as to be rotatable about the axis of the crank pin; and an external gear that meshes with the first internal gear; and a second internal gear disposed to rotate concentrically and integrally with the connecting ring, the first and second internal gears have the same number of teeth, and the external gear has the same number of teeth as the first internal gear. and the second
The number of teeth is smaller than that of the internal gear, and this double mechanism allows the center of swing of the cylinder relative to the casing to pivot to the connecting ring of the plunger inserted into this cylinder when the plunger stroke is at its maximum. Each member is positioned so that it is offset by a predetermined installation deviation angle θ in the circumferential direction around the central axis of the main shaft with respect to the reference plane A connecting the revolution center axis of the shaft and the central axis of the main shaft. Since the positional relationship is set, changes in the stroke of the plunger due to the stroke adjustment mechanism,
That is, it is possible to set arbitrary compression ratio change characteristics to a certain extent with respect to changes in the discharge or suction volume of the device.

Therefore, it is possible to operate this variable stroke radial plunger device with the compression ratio always set at a relatively high value within a predetermined volume change range (predetermined stroke change range). It can be operated with high efficiency.

Also, for example, the compressor is operated within a predetermined stroke change range of the plunger, and the compression ratio is the minimum at the maximum stroke of the plunger within this range (when the discharge volume is maximum). It is also possible to set the compression ratio change characteristic so that the compression ratio is maximum at the minimum stroke of the plunger within the range, and by setting it in this way, for example, when this device is used as an air compressor, , the compressor can be operated optimally as follows. First, when the reservoir tank is empty when the compressor starts operating, it is desirable to supply a large amount of air even if the pressure is low. In this case, the plunger stroke is maximized to supply a large amount of air. let After this,
As air gradually accumulates in the reservoir tank and the internal pressure rises, it will no longer be necessary to supply that much amount, but if the pressure is not high, it will not be possible to supply air into the tank, so gradually reduce the stroke. to supply air with a high compression ratio.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing a compressor as a variable stroke radial plunger device according to the present invention.

FIG. 2 is a sectional view showing a compressor as a variable stroke radial plunger device according to the present invention.

FIG. 3 is a schematic diagram showing the positional relationship of each rotating member during stroke adjustment by the stroke adjustment mechanism in the compressor.

FIG. 4 is a schematic diagram illustrating the operation of the double mechanism used in the compressor.

FIG. 5 is a schematic diagram showing the positional relationship between a plunger and a cylinder in the compressor.

FIG. 6 is a schematic diagram illustrating a change in the moving angle of the connecting ring due to the double mechanism when stroke adjustment is performed using the stroke adjustment mechanism in the compressor.

FIG. 7 is a partial sectional view showing a change in the top clearance when the position of the pivot axis surface is changed without stroke adjustment in the compressor.

FIG. 8 is a graph showing compression ratio change characteristics with respect to stroke changes in the compressor.

FIG. 9 is a schematic diagram showing a change in the position of each axis when stroke adjustment is performed in the compressor.

FIG. 10 is a schematic diagram showing a double mechanism using a chain.

FIG. 11 is a schematic diagram showing a different example of a double mechanism using a chain.

FIG. 12 is a sectional view showing a conventional variable stroke radial plunger device.

FIG. 13 is a cross-sectional view showing the movement of the plunger when the stroke radius is maximized in a conventional variable stroke radial plunger device.

FIG. 14 is a sectional view showing the movement of the plunger when the stroke radius is set to an intermediate value in a conventional variable stroke radial plunger device.

FIG. 15 is a graph showing compression ratio change characteristics with respect to stroke changes in a conventional variable stroke radial plunger device.

[Explanation of symbols]

1, 2 Casing 11 Main shaft 12 Crank pin 13 Eccentric collar 14 Connection ring 16 Plunger 18 Cylinder 21 Rotating sleeve 22 Sliding sleeve 31 First internal gear 32 External gear 33 Second internal gear 50 Double mechanism 51, 52 , 53, 54 Sprocket 55, 56
chain

Claims (8)

[Claims] 1. A main shaft having a casing, a main shaft rotatably disposed relative to the casing and having a crank pin eccentric from the relative rotation axis, and a main shaft rotatably mounted on the crank pin and having a main shaft rotatably mounted on the crank pin. an eccentric collar having an outer peripheral surface eccentric to the crank pin; a connecting ring rotatably mounted on the outer peripheral surface of the eccentric collar; the connecting ring extending radially outward and having an inner end pivoted to the connecting ring; a plunger,
A radial plunger device comprising a cylinder in which a cylinder hole is formed into which the plunger is inserted from the inner diameter side, and the cylinder is swingably attached to the casing with the plunger inserted into the cylinder hole. a stroke adjustment mechanism for adjusting the rotation angle of the eccentric collar on the crank pin; a first internal gear disposed concentrically with the main shaft and coupled to the casing; an external gear that is rotatably disposed on the main shaft about the axis of the crank pin and meshes with the first internal gear; and an external gear that meshes with the external gear and is concentrically integral with the connection ring. a second internal gear arranged to rotate, the first and second internal gears have the same number of teeth, and the external gear has the same number of teeth as the first and second internal gears. A variable stroke radial plunger device comprising a double mechanism with fewer teeth than the number of teeth of a gear. 2. When the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so that the reciprocating stroke of the plunger within the cylinder hole is maximized, the rotation angle of the plunger inserted into the cylinder is The center of swing of the cylinder with respect to the casing is relative to a reference plane A connecting the center axis of revolution and the center axis of the main shaft when the pivot shaft to the connecting ring revolves in accordance with the rotation of the main shaft. 2. The variable stroke radial plunger device according to claim 1, wherein the variable stroke radial plunger device is disposed so as to be offset by a predetermined installation deviation angle θ in the circumferential direction about the central axis of the main shaft. 3. When the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so as to reduce the reciprocating stroke of the plunger in the cylinder hole from the maximum state, the connecting ring of the plunger When the pivot axis to the cylinder revolves in accordance with the rotation of the main shaft, the pivot axis plane D that connects the center axis of revolution and the central axis of the main shaft is separated from the reference plane A, and the axis of the cylinder The variable stroke radial plunger according to claim 2, wherein the double mechanism is configured to move in the direction of a cylinder swing axis center plane C that connects the swing center and the central axis of the main shaft. Device. 4. The compression ratio change caused by the reciprocating stroke adjustment of the plunger by the stroke adjustment mechanism and the movement adjustment of the pivot shaft center surface D by the double mechanism accompanying this adjustment causes the reciprocating stroke of the plunger to change. 4. The variable stroke radial plunger device according to claim 3, wherein the variable stroke radial plunger device is used within a reciprocating stroke adjustment range in which the compression ratio increases as the compression ratio decreases. 5. A main shaft comprising: a casing; a main shaft rotatably disposed relative to the casing and having a crank pin eccentric from the relative rotation axis; a main shaft rotatably mounted on the crank pin; an eccentric collar having an outer peripheral surface eccentric to the crank pin; a connecting ring rotatably mounted on the outer peripheral surface of the eccentric collar; the connecting ring extending radially outward and having an inner end pivoted to the connecting ring; a plunger,
A radial plunger device comprising a cylinder in which a cylinder hole is formed into which the plunger is inserted from the inner diameter side, and the cylinder is swingably attached to the casing with the plunger inserted into the cylinder hole. a stroke adjustment mechanism that adjusts the rotation angle of the eccentric collar on the crank pin; a first external gear located concentrically with the main shaft and coupled to the casing; an internal gear that is rotatably disposed on the main shaft about the axis of the crank pin and meshes with the first external gear; and an internal gear that meshes with the internal gear and is concentrically integral with the connection ring. a second external gear arranged to rotate, the first and second external gears have the same number of teeth, and the internal gear has the same number of teeth as the first and second internal gears. A variable stroke radial plunger device comprising a double mechanism having more teeth than a gear. 6. When the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so that the reciprocating stroke of the plunger within the cylinder hole is maximized, the rotation angle of the plunger inserted into the cylinder is The center of swing of the cylinder with respect to the casing is relative to a reference plane A connecting the center axis of revolution and the center axis of the main shaft when the pivot shaft to the connecting ring revolves in accordance with the rotation of the main shaft. 6. The variable stroke radial plunger device according to claim 5, wherein the variable stroke radial plunger device is disposed so as to be offset by a predetermined installation deviation angle θ in the circumferential direction about the central axis of the main shaft. 7. A main shaft comprising: a casing; a main shaft rotatably disposed relative to the casing and having a crank pin eccentric from the relative rotation axis; a main shaft rotatably mounted on the crank pin; an eccentric collar having an outer peripheral surface eccentric to the crank pin; a connecting ring rotatably mounted on the outer peripheral surface of the eccentric collar; the connecting ring extending radially outward and having an inner end pivoted to the connecting ring; a plunger,
A radial plunger device comprising a cylinder in which a cylinder hole is formed into which the plunger is inserted from the inner diameter side, and the cylinder is swingably attached to the casing with the plunger inserted into the cylinder hole. a stroke adjustment mechanism for adjusting the rotation angle of the eccentric collar on the crank pin; a first sprocket disposed concentrically with the main shaft and coupled to the casing; and the main shaft. a second sprocket rotatably disposed above the crank pin and having a different number of teeth than the first sprocket; a first chain spanning between the first and second sprockets; a third sprocket having the same number of teeth as the second sprocket, which is arranged to rotate together with the second sprocket; and a third sprocket, which is arranged to rotate together and concentrically with the connecting ring. a fourth sprocket having the same number of teeth, and a second sprocket that is connected between the third and fourth sprockets
A variable stroke radial plunger device characterized by having a double mechanism consisting of a chain and a chain. 8. When the rotation angle of the eccentric collar is adjusted by the stroke adjustment mechanism so that the reciprocating stroke of the plunger within the cylinder hole is maximized, the rotation angle of the plunger inserted into the cylinder is The center of swing of the cylinder with respect to the casing is relative to a reference plane A connecting the center axis of revolution and the center axis of the main shaft when the pivot shaft to the connecting ring revolves in accordance with the rotation of the main shaft. 8. The variable stroke radial plunger device according to claim 7, wherein the variable stroke radial plunger device is disposed so as to be offset by a predetermined installation deviation angle θ in the circumferential direction about the central axis of the main shaft.