JPH10141206A - Cam motor device - Google Patents

Abstract

(57) [Problem] To improve durability by preventing abnormal rise in oil temperature in a cylinder corresponding to a piston while preventing rotation resistance from being generated by a piston that does not generate driving force in a high-speed mode. Plan. SOLUTION: A plurality of cylinders (5, 5, ...) radially arranged inside a cylinder block (2) rotating with respect to a cam ring (3), and a piston (6) housed in each cylinder. , A switching valve (9) for selectively switching each cylinder to a hydraulic oil supply passage (81) and a hydraulic oil supply passage (81) via a distribution valve. Prepare. When the switching valve is at the low speed position, supply and discharge of hydraulic oil are performed to all cylinders,
When the switching valve is switched to the high-speed position, hydraulic oil is supplied to and discharged from half of the cylinders, and a part of the pressure oil circulating between the other half of the cylinders is partially discharged from the bleed-off passage (911). ) To be replenished from the charge pump (16) while being bleed-off so as to be constantly replaced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cam motor device used for a traveling motor or the like of a construction machine, and more particularly, to operate at a relatively low speed by changing its motor capacity in two stages, large and small. The present invention relates to a cam motor device configured to be switchable between a low-speed mode and a high-speed mode operated at double speed thereof.

[0002]

2. Description of the Related Art Conventionally, as a cam motor device of this type, a plurality of pistons and cylinders are divided into four groups, and the distribution state of hydraulic oil to the pistons and cylinders in each of these groups is determined by switching operation of a switching valve. There is known a device which can be switched between two stages (for example, see FIG. 2 of Japanese Patent Application Laid-Open No. 55-153871). In this apparatus, by switching the switching valve to a low-speed mode, hydraulic oil is supplied to each of the selected two groups of cylinders, while each of the other two groups is connected to the oil tank. As a result, the motor capacity of the cam motor device is maximized so that the cam motor device is rotated at a relatively low speed and high output torque. Further, by switching to the high-speed mode, the hydraulic oil is supplied to each cylinder of one of the two selected groups, and the hydraulic oil is supplied from each cylinder of one of the other two groups. Is discharged, while the cylinders of the remaining two groups communicate with each other to form a closed circuit. As a result, the motor capacity of the cam motor device is reduced to half that of the low-speed mode, so that the high-speed rotation operation is performed at twice the speed of the low-speed mode.

[0003]

However, in the above-mentioned conventional cam motor device, since the two groups of cylinders to which the supply of the hydraulic oil is not performed in the high-speed mode form a closed circuit, each of the cylinders has a closed circuit. In addition, there is a risk that the pressure oil will not escape and rotational resistance will be generated, and the pressure oil will accumulate heat for the amount of mechanical loss, resulting in an abnormally high temperature, resulting in a decrease in durability.

The present invention has been made in view of such circumstances, and an object of the present invention is to minimize the rotational resistance of a piston that does not exhibit rotational driving force in a high-speed mode and to cope with the piston. An object of the present invention is to improve the durability of the cam motor device by preventing the oil temperature of the pressure oil in the cylinder from abnormally rising.

[0005]

According to a first aspect of the present invention, a cylindrical cylinder block (2) and a cam surface (3a) are formed on an inner peripheral side. A cam ring (3) disposed so as to surround the outer peripheral surface of the block (2), and a cylinder block (2) extending radially outward with respect to the center axis (X) of the cylinder block (2). A plurality of cylinders (5, 5,...) Radially arranged to open on the outer peripheral surface of 2)
And a piston (6) housed in each of the cylinders (5) so as to advance and retreat with respect to the cam surface (3a), and are relatively rotatably joined to one end surface (2a) of the cylinder block (2). The hydraulic oil supply system (15
0) is supplied to the plurality of cylinders (5, 5).
5,...), And a distribution valve (7) for distributing and supplying to each of the cylinders (6) corresponding to each of the pistons (6) on the ascending stroke toward the cam surface (3a). Each piston (6) presses the cam surface (3a) so that the other rotates with respect to one of the cylinder block (2) or the cam ring (3) fixed in a non-rotating state. It is assumed that the cam motor device is configured. In this apparatus, four communication paths (8a, 8b, 8) for supplying hydraulic oil to the plurality of cylinders (5, 5,...) Through the distribution valve (7) in four groups.
c, 8d) and these four communication passages (8a, 8b, 8).
c, 8d) is selectively connected to the supply or discharge side of the hydraulic oil of the hydraulic oil supply system (150) to switch the rotation of the cylinder block (2) or the cam ring (3) to low speed or high speed. (9) and selectively connected to specific two communication paths (8d and 8b) of the four communication paths (8a, 8b, 8c, 8d).
And a bleed-off passage (911) for bleeding the operating oil from the two communication passages (8d and 8b). In the cylinder block (2), distributed ports (21,...) Communicated with the cylinders (5) and open at equal intervals on a circumference centered on the central axis (X) on the one end surface (2a). ,...), And a distribution port (71,...) Of a multiple of 4 is provided on the joint end face (7a) of the distribution valve (7) joined to the cylinder block (2).
, 72, ..., 73, ..., 74, ... are arranged at equal intervals on the same circumference as the ports to be distributed (21, 21, ...), and the distribution ports (71, ...) are arranged. , 72, ...,
73,..., 74,...) Are grouped into the same number of four distribution port groups, and the other end of each distribution port is connected to the four communication paths (8a, 8b, 8c, 8d) and the respective distribution ports. Communicate individually with each group. And, as the switching valve (9), the four communication passages (8a, 8b, 8c,
8d), the selected two communication paths (8c, 8d or 8a, 8b) are connected to the supply side of the hydraulic oil supply system (150), and the other two communication paths (8a, 8b or 8c,
8d) is connected to the discharge side of the hydraulic oil supply system (150) at a low speed position, and one (8c or 8a) of the two selected communication paths is connected to the supply side, and One of the two communication paths (8a or 8c) is connected to the discharge side, and the other two communication paths (8d
And 8b) are connected to the discharge side of a charge pump (16) that supplies charge oil to the discharge side of the hydraulic oil supply system (150), and are connected to the bleed-off passage (911) at a high speed position. It is assumed that.

In the above configuration, when the switching valve (9) is at the low speed position, two of the four communication paths (8c, 8d or 8a, 8b) are connected to the hydraulic oil supply system (8). 150) and the other two communication paths (8a, 8b or 8c, 8d) are connected to the hydraulic oil supply system (15).
0) is connected to the discharge side. And the piston (6,
,...) For each cylinder (5) in the ascending stroke of ascending toward the cam surface (3a) from the selected two communication passages (8c, 8d or 8a, 8b). , ..., 73, ... or 72, ..., 74, ...) and the distribution ports (21, 21, ...), hydraulic fluid is supplied, and the piston (6) housed in each of these cylinders (5) is supplied. ) Presses the cam surface (3a) to rotate one of the cylinder block (2) and the cam ring (3). On the other hand, the hydraulic oil discharged by the piston (6) from each cylinder (5) in the descending stroke in which the piston (6, 6,...) Descends toward the rotation axis (X) is distributed to the ports to be distributed (21, 21). , ...) and the distribution ports (72, ..., 74, ... or 71, ..., 73, ...) and the other two communication paths (8a, 8b or 8c, 8).
From d), it is returned to the discharge side of the hydraulic oil supply system (150). That is, the cam motor device is rotated in the low-speed mode of relatively low speed and high output torque with the maximum motor capacity. When the switching valve (9) is at the high-speed position, one of the two selected communication paths (8c, 8d or 8a, 8b) (8c or 8a).
Is connected to the supply side of the hydraulic oil supply system (150), and
One communication path (8a or 8c) of the other two communication paths (8a, 8b or 8c, 8d) is connected to the discharge side of the hydraulic oil supply system (150), and the remaining two communication paths are connected. The passages (8d and 8b) are provided with a hydraulic oil supply system (150).
Pump (1) that supplies charge oil to the discharge side of
6) and connected to the bleed-off passage (911). Therefore, the number of pistons (6, 6,...) Receiving the supply of hydraulic oil is reduced to half of the low-speed mode, and the cam motor device has a motor capacity reduced to half and operates at twice the speed and 2 × in the low-speed mode. It is rotated in a high speed mode with a one-output torque. At this time, the pressure oil in each cylinder (5) connected to each other via the remaining two communication paths (8d and 8b) is circulated through these two communication paths (8d and 8b). At the same time, a part of the bleed-off is bleed-off through the bleed-off passage (911), so that the hydraulic pressure in each of the cylinders (6) is prevented from rising, and rotation resistance is prevented from being generated. On the other hand, since the same amount of pressure oil as the pressure oil to be bleed-off is supplied from the charge pump (16), a part of the pressure oil circulating between the cylinders (5) is always replaced. become. This makes it possible to prevent the oil temperature from rising abnormally and improve the durability of the cam motor device.

According to a second aspect of the present invention, the cam ring (3) in the first aspect of the present invention is fixed in a non-rotating state with respect to the main body side (13) of the cam motor device, and the cylinder block (2) is fixed. , And rotatably supported on the main body side (13).

In the case of the above configuration, the configuration of the cylinder block (2) and the configuration of the cam ring (3) in the first aspect of the invention are specifically specified. That is, the cam ring (3) is fixed to the main body side (13) of the cam motor device in a non-rotating state, and the cylinder block (2) is relatively rotated with respect to the cam ring (3). 3), the rotational driving force is reliably output from the switching valve (9) according to the first aspect of the invention. The switching valve (9) is moved to the low-speed position and the high-speed position by the pressure oil supplied from the charge pump (16). And it can be switched to

In the case of the above configuration, a configuration for switching the switching valve (9) according to the first aspect of the present invention is specifically specified, and charge oil is supplied to the discharge side of the hydraulic oil supply system (150). The switching valve (9) is reliably operated by the pressure oil supplied from the charge pump (16) for performing the operation. Thus, the switching operation can be performed without providing a special driving source for the switching operation of the switching valve (9).

According to a fourth aspect of the present invention, there is provided a switching valve (9) according to the first or third aspect of the present invention, wherein a valve element (92) formed in a column shape and a valve element (92) formed in the valve element (92). And
One end is connected to the charge pump (16), and the other end is connected to the bleed-off passage (9) through the throttle (927).
11) and a supply passage (926) communicating with the switching valve (926). The supply passage (926) is provided with an opening opening on the peripheral surface of the valve element (92), and the opening is provided with the switching valve (926). When 9) is at the high speed position, the hydraulic oil supply system (150)
Are arranged so as to open toward two communication paths (8d and 8b) that are not connected to either the supply side or the discharge side.

In the above configuration, when the switching valve (9) is at the high speed position, the two communication passages (8d) not connected to either the supply side or the discharge side of the hydraulic oil supply system (150).
And 8b) flows out to the bleed-off passage (911) via the supply passage (926) formed in the valve body (92) of the switching valve (9), while the charge pump (1).
The pressure oil from 6) is replenished to the two communication passages (8d and 8b) via the supply passage (926), whereby the operation according to the first aspect of the present invention is reliably obtained.
Further, since the throttle portion (927) is provided on the supply passage (926) on the side of the bleed-off passage (911), the valve element (92) made of the charge oil supplied to the supply passage (926) is formed. Switching from the low speed position to the high speed position becomes possible. Therefore, it is possible to make the hydraulic circuit for supplying the pressure oil from the charge pump (16) compact, and thereby to make the whole apparatus compact.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows a cam motor device according to an embodiment of the present invention, wherein 1 is a casing main body formed in an annular shape,
Reference numeral 2 denotes a cylinder block formed in a thick cylindrical shape, reference numeral 3 denotes a cam ring disposed around the outer peripheral surface of the cylinder block (2), and reference numeral 4 denotes an end cap. Also, 5,
(See FIG. 2) are a plurality of cylinders arranged in the cylinder block (2), and 6 is each of the cylinders (5)
The piston 7 housed in the inside is a distribution valve for distributing and supplying the hydraulic oil to each of the cylinders (5). In addition, 8
Reference numerals a, 8b, 8c and 8d denote annular communication passages as four communication passages arranged around the outer peripheral surface of the distribution valve (7), and 9 operates these annular communication passages (8a, 8b,...). A supply / discharge operation valve 10 as a switching valve for switching connection to an oil supply side or a discharge side is an output shaft. The cam motor device is provided, for example, on a vehicle body such as a construction machine and drives wheels, crawlers, and the like.

The casing body (1) is arranged coaxially with the rotation axis (X) of the output shaft (10), and is arranged on one side in the direction of the rotation axis (X) (left side in FIG. ), A substantially conical casing cover (1)
1) and a plurality of bolts (11a, 11a,...), While a plurality of bolts (12, 12,...)
2 (see FIG. 2), the cam ring (3) is interposed therebetween and fastened to the end cap (4), and constitutes a casing (13) which is a main body of the cam motor device. Tapered roller bearings (111, 41) disposed on the casing cover (11) and the end cap (4), respectively, with the output shaft (10) penetrating the casing (13) left and right. , And are freely rotatable. Also, mounting flanges (14, 14, ...) are provided on the outer peripheral surfaces of the casing body (1) and the end cap (4) so as to protrude outward, and these mounting flanges (14, 14, ..), The casing (13) is fixed to the vehicle body.

The cylinder block (2) is connected to an outer peripheral surface of the output shaft (10) by, for example, a spline connection, and is disposed so as to rotate coaxially and integrally with the output shaft (10). As shown in FIG. 2, a plurality of and even (eight in the example shown) cylinders (5, 5,...)
Are arranged radially around the rotation axis (X) and at equal intervals in the circumferential direction, extend outward in the radial direction of the cylinder block (2), and open to the outer peripheral surface.
A piston (6) is accommodated in each of these cylinders (5), and each of these pistons (6)
Is guided by the cam surface (3a) while rolling the roller (61) disposed at the tip along the cam surface (3a) formed inside the cam ring (3). It moves forward and backward in the cylinder (5). further,
The cylinder block (2) is communicated with each of the cylinders (5), and at one end surface (2a) (right end surface) of the cylinder block (2) on the circumference around the rotation axis (X). Are provided with eight ports to be distributed (21, 21,...) That open at equal intervals.

As shown in FIG. 2, the cam ring (3) has, on its cam surface (3a), a predetermined number (six in the illustrated example) determined by the relationship between the number and arrangement of the pistons. The convex portions (31, 31, ...) and the concave portions (32, 32,
…) Are formed at equal intervals and alternately in the circumferential direction,
The eight pistons (6, 6) for this cam surface (3a)
6,...), The piston (6) at the upper right position in FIG.
In the eighth case, the first and fifth pistons (6) are at substantially the bottom points of the recesses (32), and the second and sixth pistons (6) are at the bottom of the protrusions (31) and the recesses (32). 32) at the downstream halfway point (i.e., on the downstroke).
Each of the pistons (6) has a substantially apex of the convex portion (31), and each of the fourth and eighth pistons (6) has an upward intermediate point between the convex portion (31) and the concave portion (32). (I.e., on the upstroke). Therefore, mainly by supplying hydraulic oil so that the fourth and eighth pistons (6) press the cam surface (3a), the cylinder block (2) moves around the central axis (X). Counterclockwise in the figure (direction of arrow)
The cylinder block (2) further rotates by supplying hydraulic oil mainly to the third and seventh pistons, and the rotation causes the second block to move over the convex portion (31). By distributing and supplying hydraulic oil in order such as supplying hydraulic oil to each of the sixth pistons, the cylinder block (2) and the output shaft (10) are continuously driven to rotate. I have.

The distribution valve (7) is formed in a substantially cylindrical shape, and has one end face (7a) (left end face: hereinafter, referred to as a joint end face) which is opposed to the right end face (2a) of the cylinder block (2). It is arranged so as to be rotatably joined, and is fixed to the end cap (4) in a non-rotating state while being fitted inside the inner peripheral portion. An annular recess formed in the inner peripheral surface of the end cap (4) so as to open opposite to the entire outer peripheral surface of the distribution valve (7) of the output shaft (10). Four are formed in the longitudinal direction (left-right direction), and these annular concave portions and the outer peripheral surface of the distribution valve (7) sequentially form the second, fourth, and fourth from the left.
The first and third four annular communication passages (8a, 8b, 8c,
8d) is defined. Then, the joining end face (7
3A, as shown in FIG. 3, the distribution ports (71,...) of the multiple (12 in the example shown) of the number of the projections (31,...) or the depressions (32,...) of the cam surface (3a). ..., 72, ..., 7
, 74,...) Are provided on the right end face (2a) of the cylinder block (2).
,..) Are provided at equal intervals on the same circumference as these distributed ports (21, 21,...).

The distribution ports (71,..., 72,.
, 74,...) Are a first distribution port group composed of first distribution ports (71, 71,...) Disposed every third in the circumferential direction, and the first ports described above. The second distribution ports (72, 72) disposed adjacent to the cylinder block (2) in the normal rotation direction (counterclockwise in FIG. 3).
72), and a third distribution port (73, 73,...) Arranged adjacent to the second distribution ports in the same direction as above. The third distribution port group configured and the fourth distribution port group disposed adjacent to the third distribution port in the same direction as described above.
The same number of distribution ports (71,...) As the fourth distribution port group constituted by the distribution ports (74, 74,.
72, ..., 73, ..., 74, ...). And each of the first
The end (right end) of the distribution port (71) opposite to the cylinder block (2) extends in the longitudinal direction of the output shaft (10) to the position of the first annular communication passage (8c). 1
Similarly, each of the second distribution ports (72) is connected to the second annular communication path (8a), and each of the third distribution ports (73) is connected to the third annular communication path (8d). )When,
Each of the fourth distribution ports (74) is connected to a fourth annular communication passage (8).
b), respectively.

The four annular communication paths (8a, 8b,...)
Among them, the first annular communication passage (8c) is provided with the supply passage (81).
The main pump (15) is connected to the main pump (15) to receive a supply of hydraulic oil discharged from the main pump (15). On the other hand, the second annular communication passage (8a)
Is connected to the main pump (1) through a discharge passage (82).
5) and is configured to recirculate the hydraulic oil discharged from the cylinder block (2) side to the main pump (15). Then, a closed circuit constituted by the main pump (15), the supply passage (81), the discharge passage (82), and the like, and a passage on the low pressure side for replenishing leakage of hydraulic oil from the closed circuit are provided. A hydraulic oil supply system (1) is provided by a charge pump (16) for supplying charge oil.
50) are configured. In addition, the main pump (1)
5) is configured to be able to reverse the suction direction and the discharge direction of the hydraulic oil, and to supply the hydraulic oil to the discharge passage (82) to thereby output the output shaft (10) of the cam motor device.
Can be reversed.

The supply / discharge operation valve (9) includes a valve chamber (91) having a circular cross section formed inside the end cap (4), and a longitudinal direction (lateral direction) within the valve chamber (91). ) And a cylindrical valve element (92) slidably housed therein. As shown in detail in FIGS. 4 and 5, the valve chamber (91) includes first, second, third, and fourth valves arranged in order from the left side (hereinafter, simply referred to as left side) in FIG. Four enlarged portions (91a, 91b, 91c, 91
d) and these four enlarged portions (91a, 9a).
1b, 91c, 91d) are the end caps (4)
The four communication passages (83a, 83b, 83
c, 83d) to form four annular communication paths (8a, 8b, 8).
c, 8d). Further, the right side of the valve chamber (91) in the figure (hereinafter, simply referred to as right side).
A cylinder portion (91e) is formed at the end of
When the switching valve (161) is at the right position, pressure oil is supplied from the charge pump (16) via the charge oil supply passage (93), and the valve element (92) is operated. Further, a bleed-off passage (911) is formed at the left end of the valve chamber (91) so as to open toward the inside of the casing (13) containing the cylinder block (2). Through.

The valve element (92) has first, second and third large-diameter portions (921, 9) formed in order from the left side.
22, 923) and these large diameter portions (921, 922,
923) formed between the small diameter portions (924, 9
25), and is open to the right end face,
A supply passage (926) extending in the longitudinal direction (left-right direction) to the vicinity of the left end surface, and the bleed-off passage (911) and the supply passage (92) at the left end surface.
6), and a throttle portion (92) penetratingly formed so as to be able to communicate therewith.
7). Further, the supply passage (926)
The second large-diameter portion (922) and the third large-diameter portion (92
On the outer peripheral surface of 3), 4
It has openings formed at each location.

Then, as shown in FIG. 4, the valve element (92) is pressed to the right by the urging force of the spring (94) and is positioned at the low speed position.
The third enlarged diameter portion (91c) and the fourth enlarged diameter portion (91d) communicate with each other, and the first enlarged diameter portion (91a) and the second enlarged diameter portion (91b) communicate with each other. It is configured. Therefore, when the valve element (92) is at the low speed position, the first and third annular communication passages (8c and 8d) communicate with the supply passage (81), and the second and fourth annular communication passages are formed. The communication passages (8a and 8b) communicate with the discharge passage (82).

As shown in FIG. 5, the valve element (92) receives the charge pressure supplied to the cylinder portion (91e) and moves to the left against the urging force of the spring (94). In this high-speed position, the first enlarged diameter portion (91a) and the third enlarged diameter portion (91c)
Each of the second enlarged diameter portion (91b) and the fourth enlarged diameter portion (91d) communicates with each other via a supply passage (926) while being blocked from any other enlarged diameter portion. The right side of the supply passage (926) is connected to the discharge side of the charge pump (16), while the left side is
Bleed-off passage (911) through the throttle (927)
And it will be in a connected state. The first annular communication path (8c) communicates with the supply path (81), the second annular communication path (8a) communicates with the discharge path (82), and the third annular communication path (82). (8d) and the fourth annular communication passage (8b) are communicated with each other, and a predetermined amount of hydraulic oil flows from the third and fourth annular communication passages (8d and 8b) to the supply passage (926) and the bleed-off passage. (911) and flows into the casing (13), while the same amount of pressure oil flows out of the charge pump (1).
6) Replenishment is done from the side. Here, the pressure oil that has flowed into the casing (13) through the bleed-off passage (911) flows into the casing (13).
While cooling the inside, the oil is returned to the oil tank (19) through a drain pipe (not shown). Further, the flow rate of the pressure oil passing through the bleed-off passage (911) is set to a predetermined flow rate that can prevent the rise in the oil temperature by constantly changing the flow rate of the pressure oil.

Accordingly, the valve body (9) of the supply / discharge operation valve (9) is provided.
2) is at the low speed position (see FIG. 4), the hydraulic oil from the supply passage (81) is supplied to the third and fourth enlarged diameter portions (91c and 91d) and the first and third annular communication passages (8c). And 8
d) through the first and third six distribution ports (7
1,73) to make them on the high pressure side,
The other six second and fourth distribution ports (72, 74)
Are the second and fourth annular communication paths (8a and 8b) and the first
And, it is communicated with the discharge passage (82) through the second enlarged diameter portions (91a and 91b) so as to be on the low pressure side. Conversely, when the valve element (92) of the supply / discharge operation valve (9) is at the high-speed position (see FIG. 5), the operating oil from the supply passage is supplied to the third enlarged portion (91c) and the first annular portion. Communication passage (8
c) to the first three distribution ports (71), which are brought to the high pressure side, while the second three distribution ports (72) are connected to the second annular communication passage (8a). ) And the first enlarged diameter portion (91a) and communicated with the discharge passage on the low pressure side, and at the same time, the third and fourth six distribution ports (7).
3, 74) are the third and fourth annular communication passages (8d and 8).
b) and the supply passage (926) through the second and fourth enlarged diameter portions (91b and 91d), the pressurized oil circulates between them and a part of the pressurized oil is supplied to the supply passage (926). It is always exchanged via the passage (926).

In FIG. 1, reference numeral 17 denotes an output shaft (10).
This is a negative brake mechanism that restricts the rotation of. The negative brake mechanism (17) is connected to the output shaft (1).
0) a plurality of pressure rings fixed on the outer peripheral surface;
A pressure plate interposed between the pressure rings and fixed to the inner peripheral side of the casing body (1), and the above-mentioned pressure plate is not supplied with pressure oil from the charge pump (16). The pressure ring and the pressure plate are pressed against each other by the urging force of the disc spring (18), so that the output shaft (10) is moved by the sliding frictional force between them to the casing body (1).
Is configured to be constrained in a non-rotating state with respect to
On the other hand, the pressure ring and the pressure plate are separated from each other by receiving the supply of the pressure oil from the charge pump (16), so that the output shaft (10) is maintained in a freely rotatable state.

Next, the operation, operation and effect of the cam motor device according to the above embodiment will be described. First, the charge pump (16) is operated to supply the pressure oil to the negative brake mechanism (17), and the restrained state of the output shaft (10) by the negative brake mechanism (17) is released.
Next, the operating oil is supplied to the supply passage (81) with the main pump (15) in an operating state.

When the cam motor device is rotated in the low-speed mode, the switching valve (161) is switched to the left position to supply pressure oil from the charge pump (16) to the supply / discharge operation valve (9). Cut off. As a result, the valve element (92) of the supply / discharge operation valve (9) is positioned at the low speed position (see FIG. 4), and the first and third total of six distribution ports (71, 73) are operated by the operating oil. And the supply side of
Second and fourth total of six distribution ports (72, 74)
At the discharge side of the hydraulic oil. Then, half of the eight cylinders (5, 5,...), That is, four cylinders (5, 5,...: 3, 4, 7, and 8 in FIG. Hydraulic oil is supplied to the four cylinders, and the piston (6) housed in each of the cylinders (5) generates a driving force, so that the cylinder block (2) and the output shaft (10) Rotate together. Then, with this rotation, the positional relationship between the cylinder block (2) and the distribution valve (7) changes, and then the four cylinders (5, 5,..., 2 in FIG.
Hydraulic oil is supplied to the third, sixth and seventh cylinders, and the cylinder block (2) further rotates. This is repeated, and the cylinder block (2) and the output shaft ( 10) rotates continuously. on the other hand,
Hydraulic oil is discharged from each of the four cylinders (5) in the descending stroke by the piston (6) to form a discharge passage (82).
To the suction side of the main pump (15).
Thus, in the low-speed mode, the cam motor device
The motor capacity is maximized and the motor is rotated at a relatively low speed and high output torque.

In order to rotate the cam motor device in a high-speed mode, the switching valve (161) is switched to the right position and the charge / discharge operation valve (9) is connected to the charge pump (16).
Supply pressure oil from As a result, the valve element (92) of the supply / discharge operation valve (9) is switched to the high-speed position (see FIG. 5), and the first three distribution ports (71) are connected to the supply side of the hydraulic oil. 2, the three distribution ports (72) are switched to the hydraulic oil discharge side, and the third and fourth
The distribution ports (73, 74) are connected to each other. Then, each of the two cylinders (5: 5: 5: 5: 5) of the four cylinders (5,5,.
Hydraulic oil is supplied to the fourth and seventh cylinders in FIG. 2, and the piston (6) housed in each of the cylinders (5) generates a driving force, while the piston (6) is in the descending stroke. Hydraulic oil is discharged from two half cylinders (5: two first and sixth cylinders in FIG. 2) of a certain four cylinders (5, 5,...).
In each of the five cylinders (5: the second, third, fifth and eighth cylinders in FIG. 2), the piston (6)
Does not generate a driving force only by reciprocating in each cylinder (5) along the cam surface (3a). Accordingly, the cam motor device is rotated at a relatively high speed and a low output torque with the motor capacity being half that of the low speed mode.

Here, in the high-speed mode, the pressure oil in each cylinder (5) that is not connected to either the supply side or the discharge side of the hydraulic oil and does not generate a driving force is the third and fourth hydraulic oil.
The two annular communication passages (8d and 8b) and the supply passage (92
6), and a part of the pressure oil is returned to the oil tank (19) via the bleed-off passage (911). Refilled from the pump (16) and constantly replaced. For this reason, it is possible to prevent the occurrence of rotational resistance due to an increase in oil pressure, and to prevent an abnormal increase in oil temperature, thereby improving the durability of the cam motor device.

Further, in the above cam motor device, when the supply / discharge operation valve (9) is switched to the high-speed position, the third distribution ports (73, 73,...) And the fourth distribution ports (74, 7).
,...) Are reliably connected by a supply passage (926) formed in the valve element (92) of the supply / discharge operation valve (9), and the third and fourth distribution ports (7,
3,..., 74,...) Are surely replaced through the supply passage (926), so that the pressure oil from the charge pump (16) is removed. The hydraulic circuit for supplying can be made compact, thereby making the whole apparatus compact.

Next, when the cam motor device is reversed, the suction direction and the discharge direction of the hydraulic oil in the main pump (15) are reversed so that the hydraulic oil is supplied to the discharge passage (82). I do. When the reverse rotation is performed in the low-speed mode, the supply / discharge operation valve (9) is set to the low-speed position as in the case of the normal rotation in the low-speed mode, and the second and fourth distribution ports (72) in total are provided. , 74) on the hydraulic oil supply side, and a total of six first and third distribution ports (7
1, 73) to the hydraulic oil discharge side,
Of the four cylinders (5,5, ...) on the upstroke
While supplying hydraulic oil to each of the cylinders (5),
Hydraulic oil is discharged from each of the four cylinders (5) in the downward stroke, and the cam motor device can be rotated at a relatively low speed and high output torque. When the cam motor device is operated in reverse in the high-speed mode,
The supply / discharge operation valve (9) as in the case of the normal rotation in the high-speed mode.
To the high-speed position, and the second three distribution ports (7
2) is switched to the supply side of hydraulic oil, the first three distribution ports (71) are switched to the discharge side of hydraulic oil, and the third and fourth distribution ports (73, 74) are totally six. And each of these distribution ports (73, 74)
Is supplied with pressure oil from the charge pump (16). As a result, the four cylinders (5, 5,...) On the ascending stroke
The hydraulic oil is supplied to each of the two cylinders (5) in the half of the four cylinders (5,
, 5), the hydraulic oil is discharged from each of the two cylinders (5), and the cam motor device can be rotated at a relatively high speed with a low output torque.

Compared with the conventional cam motor device shown in FIG. 6 in the case of the reverse rotation operation, in this conventional cam motor device, a plurality of pistons and cylinders are divided into three groups, and three pistons and cylinders are provided for each group. It is configured to distribute and supply the hydraulic oil through the two communication paths (108a, 108b, 108c). Specifically, 12 distribution ports are replaced with 6 first distribution ports (not shown), 3
And two third distribution ports (not shown) and three third distribution ports (110).
The first communication path (108a) is connected to each of the first distribution ports, and the third communication path (108) on the right side (hereinafter, simply referred to as right side) in the figure with the second communication path (108b) in the middle.
c) are connected to the second and third distribution ports, respectively, and the first communication path (108a) is connected to the hydraulic oil discharge path, while the third communication path (108) is connected to the third communication path (108).
c) is communicated with the hydraulic oil supply passage. Then, in the case of normal rotation in the high-speed mode, the third communication path (108
c), the hydraulic oil is supplied to each of the three third distribution ports (110) to be on the high pressure side, while the supply / discharge operation valve (10)
9), the six first distribution ports and the three second distribution ports are connected to the low pressure side via the first communication path (108a) and the second communication path (108b) communicated with each other. It is supposed to be. For this reason, when reverse rotation is performed in the high-speed mode, the first communication passage (108a) and the second communication passage (108b) are opposite to the above-described normal rotation.
Receiving the hydraulic oil supplied from the discharge passage, the six first distribution ports and the three second distribution ports are set to the high pressure side while the third communication path (10
8c) is connected to the supply passage, whereby 3
Each third distribution port (110) will be on the low pressure side. Therefore, high-pressure hydraulic oil is supplied not only to the cylinder that generates the driving force for the reverse rotation drive but also to the cylinder that does not generate the driving force for the reverse rotation drive, and as a result, the rotational resistance is significantly increased. In addition, the adverse thermal effect increases. On the other hand, in the cam motor device according to the embodiment, when the reverse rotation is performed in the high-speed mode, the hydraulic fluid is supplied from the discharge passage (82) to the second annular communication passage (8a) (see FIG. While the first annular communication passage (8c) is connected to the supply passage (81) to be on the low pressure side, and the third and fourth two passages are the same as in the case of normal rotation in the high-speed mode. Annular communication path (8d
And 8b) are supplied with pressure oil from the charge pump (16). Therefore, pressure oil having substantially the same pressure as the discharge side of the hydraulic oil supply system (150) is supplied to the cylinders (5) that do not generate the driving force, and the piston (5) The rotation resistance associated with the operation 6) can be reduced as compared with the conventional case to improve the efficiency, and at the same time, the adverse thermal effect can be reduced.

<Other Embodiments> The present invention is not limited to the above embodiments, but includes various other embodiments. That is, in the above embodiment,
As a configuration of the cam motor device, a cam ring (3) is fixed to a casing (13), and an output shaft (1) is attached to a cylinder block (2) that rotates relative to the cam ring (3).
However, the present invention is not limited to this. For example, the cylinder block may be fixed to the apparatus body and the annular casing including the cam ring may be rotated with respect to the cylinder block. .

In the above embodiment, six projections (31) and six depressions (32) are formed on the cam surface (3a) of the cam ring (3), and eight pistons (6) are correspondingly formed. , 6,...) Are provided, but the invention is not limited to this. For example, the number of protrusions and recesses of the cam ring may be other than six, and correspondingly, pistons other than eight may be provided. You may.

In the above embodiment, the bleed-off passage (9
Although the pressure oil that has passed through 11) passes through the casing (13) and is returned to the oil tank (19), the invention is not limited thereto, and the oil tank (19) does not pass through the casing (13). ).

[0036]

As described above, according to the cam motor device according to the first aspect of the present invention, when the switching valve (9) is at the high speed position, the supply or discharge side of the hydraulic oil supply system (150) is provided. The pressurized oil in each cylinder (5) that is not connected to either of these two communication passages (8d and 8d).
By circulating through the b) and partially bleeding off through the bleed-off passage (911), the hydraulic pressure in each of the cylinders (6) is prevented from rising, thereby preventing the occurrence of rotational resistance. be able to. Further, by replenishing the same amount of pressure oil as the recirculated pressure oil from the charge pump (16), a part of the pressure oil circulated between the cylinders (5) can be always replaced. Thereby, the oil temperature can be prevented from rising abnormally, and the durability of the cam motor device can be improved.

According to the second aspect of the invention, the configurations of the cylinder block (2) and the cam ring (3) in the first aspect of the invention are specifically specified, and the output shaft (1
0) can reliably output the driving force.

According to the third aspect of the invention, the switching valve (9) is operated by the operating oil supplied from the charge pump (16) for supplying the pressure oil to the discharge side of the operating oil supply system (150). The operation can be surely performed, whereby the effect according to the first aspect of the present invention can be reliably obtained.

According to the fourth aspect of the invention, in addition to the effect of the third aspect of the invention, the supply passage (926)
Squeezing section (927) on the side of the bleed-off passage (911)
, The valve element (92) can be switched from the low-speed position to the high-speed position by the charge oil supplied to the supply passage (926), whereby the pressure oil from the charge pump (16) can be removed. The hydraulic circuit for supplying can be made compact, and the whole apparatus can be made compact.

[Brief description of the drawings]

FIG. 1 is a partially cutaway view showing an embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a perspective view showing a configuration of a distribution port.

FIG. 4 is an enlarged sectional view showing a configuration of a supply / discharge operation valve.

FIG. 5 is a diagram corresponding to FIG. 4 when in a high-speed position.

FIG. 6 is a diagram showing a configuration example of a supply / discharge operation valve in a conventional cam motor device.

[Explanation of symbols]

2 Cylinder block 2a One end surface of cylinder block 3 Cam ring 3a Cam surface 5 Cylinder 6 Piston 7 Distribution valve 7a One end surface of distribution valve (joining end surface) 8a Second annular communication passage (communication passage) 8b Fourth annular communication passage (communication passage) 8c First annular communication path (communication path) 8d Third annular communication path (communication path) 9 Supply / discharge operation valve (switching valve) 13 Casing (body) 16 Charge pump 21 Ports to be distributed 71, 72, 73, 74 Distribution Port 92 Valve body of switching valve 150 Hydraulic oil supply system 911 Bleed-off passage 926 Supply passage 927 Narrow portion of supply passage X Rotary shaft (center axis of cylinder block)

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Toshihiro Naruse 1-1, Nishiichitsuya, Settsu-shi, Osaka Daikin Industries, Ltd. Yodogawa Works (72) Inventor Masaaki Suhara 1-1-1, Nishiichitsuya, Settsu-shi, Osaka Daikin Industries Inside Yodogawa Works

Claims (4)

[Claims] A cam ring (3) having a cylindrical cylinder block (2) and a cam surface (3a) formed on the inner peripheral side, and disposed around the outer peripheral surface of the cylinder block (2). A plurality of cylinders (5) extending radially outward with respect to the cylinder block (2) around the center axis (X) thereof and radially arranged to open on the outer peripheral surface of the cylinder block (2); , 5,...), A piston (6) housed in each of the cylinders (5) so as to advance and retreat with respect to the cam surface (3a), and one end surface (2a) of the cylinder block (2). The hydraulic oil supplied from the hydraulic oil supply system (150), which is disposed so as to be rotatably connected to the cam surface (3a) of the plurality of cylinders (5, 5,...), Moves upward. Corresponding to each piston (6) in A distributing valve (7) for distributing and supplying to the cylinder (6), wherein each of the pistons (6) in the upward stroke presses the cam surface (3a) to be fixed in a non-rotating state. In a cam motor device configured so that one of the cylinder block (2) and the cam ring (3) rotates with respect to the other, a plurality of cylinders (5, 5, 5) are provided via the distribution valve (7).
..) And four communication paths (8a, 8b, 8c, 8d) for supplying hydraulic oil in four groups, and the four communication paths (8a, 8b, 8c, 8d) to a hydraulic oil supply system ( 150) a switching valve (9) selectively connected to the supply or discharge side of the hydraulic oil to switch the rotation of the cylinder block (2) or the cam ring (3) to low speed or high speed; Bleed-off which is selectively connected to specific two communication paths (8d and 8b) of (8a, 8b, 8c and 8d) and bleeds off hydraulic oil from these two communication paths (8d and 8b). A passage (911), and the cylinder block (2) is communicated with each cylinder (5) and is equidistantly arranged on the circumference centered on the central axis (X) at the one end surface (2a). Port (2)
., Are provided in the distribution valve (7). The distribution ports (71,..., 72,...) Are multiples of 4 on the joint end face (7a) with the cylinder block (2). , 73,..., 74,...) Are disposed on the same circumference as the distributed ports (21, 21,.
, 72, ..., 73, ..., 74, ...) are grouped into the same number of four distribution port groups, and the other end of each distribution port is connected to the four communication paths (8a, 8b, 8c, 8).
d) for each of the distribution port groups, and the switching valve is connected to the four communication paths (8a, 8b, 8c,
8d), the selected two communication paths (8c, 8d or 8a, 8b) are connected to the supply side of the hydraulic oil supply system (150), and the other two communication paths (8a, 8b or 8c,
8d) is connected to the discharge side of the hydraulic oil supply system (150) at a low speed position, and one (8c or 8a) of the two selected communication paths is connected to the supply side, and One of the two communication paths (8a or 8c) is connected to the discharge side, and the other two communication paths (8d
And 8b) are connected to the discharge side of a charge pump (16) that supplies charge oil to the discharge side of the hydraulic oil supply system (150), and the bleed-off passages (911 and 92) are connected.
And a high-speed position connected to (7). 2. The cam ring (3) according to claim 1, wherein the cam ring (3) is provided on a main body side (13) of the cam motor device.
And a cylinder block (2) rotatably supported by the main body side (13). 3. The cam motor according to claim 1, wherein the switching valve (9) is configured to be switched between a high-speed position and a low-speed position by pressure oil supplied from a charge pump (16). apparatus. 4. The switching valve (9) according to claim 1, wherein the switching valve (9) is formed in a column-shaped valve element (92), and is formed in the valve element (92), and one end side of the charge pump (16). ) And a supply passage (926) whose other end communicates with the bleed-off passage (911) through a throttle (927). The supply passage (926) is provided with the valve body (926). 92), the opening is provided in the peripheral surface of the hydraulic oil supply system (150) when the switching valve (9) is at the high speed position.
The cam motor device is provided so as to open toward two communication paths (8d and 8b) not connected to either the supply side or the discharge side of the cam.