JPH0438120Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an improvement of a ring gear of a reduction gear used in a crawler vehicle traveling device.

[Conventional technology]

A conventional speed reducer of this type has been filed as U.S. Pat. No. 60-142211 filed by the applicant.
In this reducer, a ring gear having a flange to which a sprocket that meshes with a crawler is attached is rotatably attached to a casing that has a hydraulic motor, and a wheel gear that meshes with and rotates with the ring gear is installed inside the ring gear and is connected to the hydraulic motor. The crankshaft is rotated by a crankshaft and is rotatably provided in the casing.The crankshaft is rotatably provided in the casing, and is provided for rocking motion.The wheel gear has a structure in which a plurality of pins fixed to the casing pass through the crankshaft. In this reducer, the number of teeth on the wheel gear is smaller than the number of teeth on the ring gear, and when the crankshaft of the wheel gear rotates once, the ring gear is rotated by the difference in the number of teeth between the ring gear and the wheel gear. It is. (The specific structure is almost similar to that shown in FIG. 1, which is an embodiment of the present invention, so please refer to the explanation of the embodiment described later.) The above reduction gear has a ring gear. By making the tooth profile of the wheel gear and wheel gear an involute tooth profile and setting the engagement ratio to 1 or less, heat treatment (hardening treatment) is applied to only the tooth portion of both the wheel gear and ring gear, and distortion due to the heat treatment of the tooth profile portion is reduced. is to adjust and absorb the breakdown.

[Problem that the invention attempts to solve]

The conventional reduction gear described above has a ring gear as shown in FIG. 4. In the ring gear L shown in FIG. 4, the gear portion L1 and the flange portion L2 are integrally formed. The gear part L1 is formed of a cylindrical part L11 and an involute tooth profile part L12 (see FIG. 2). The flange part L2 has bearings B1 and B attached to the casing part CA (see Figure 1).
Inner holes L21, L22 to be attached via 2
A flange L23 to which a sprocket SP (see FIG. 1) is fixed is integrally formed.

When the toothed portion L12 of the ring gear L formed in this way is hardened by heat treatment, due to the difference in wall thickness between the flange portion L2 and the gear portion L1,
The tip L1 of the gear part L1 centering on the connecting part L14
3 spreads outward as shown by the broken line L13'.
In other words, the gear portion L1 is deformed into a tumble shape. For this reason, the tooth profile of the gear is an involute tooth profile, other tooth profiles, pericycloid parallel curve tooth profile (Japanese Utility Model Publication No. 121174, 1983), and circular arc tooth profile (Japanese Patent Application Laid-Open No. 1983-121174).
No. 71459), even if the meshing condition is improved and tooth profile interference is prevented, if the gear part deforms into a rough shape during hardening of the ring gear, the wheel gear will be pushed outward and come into contact with the lid, reducing operating efficiency. This was a decrease.

The present invention solves the above problems.

[Means for solving problems]

The means of the present invention for solving the above problems is to provide a rotatable ring gear having a flange to which a sprocket is attached to a casing in which a hydraulic motor is provided, and to install the hydraulic motor within this ring gear. A wheel gear is rotatably attached to the driven eccentric shaft and has a tooth profile that meshes with the tooth profile of the ring gear, and a pin fixed to the casing passes through the wheel gear. In a reducer in which the tooth profile of the ring gear is an involute tooth profile, the ring gear is divided into a flange part and a gear part having a substantially uniform wall thickness, and the tooth profile part of the gear part is heat treated, and then the flange part and the gear part are separated. The gear part is welded to form an integral structure.

[Effect]

According to the present invention, only the gear part of the ring gear needs to be heat treated, and since the wall thickness of the gear part is made uniform, the temperature distribution of the gear part during heat treatment is the same, so there is no shrinkage after heat treatment. occurs in almost the same state, and the entire gear portion only becomes smaller on average, and it is possible to prevent it from deforming into a lumpy shape.

〔Example〕

1 to 3 show an embodiment of the present invention.
In the drawings, FIG. 1 is a sectional view thereof, FIG. 2 is a sectional view taken along the line AA in FIG. 1, and FIG. 3 is a partially enlarged view of the ring gear portion L.

In this embodiment, the present invention is applied to a hydraulic motor with a speed reducer for driving a crawler.

The hydraulic motor GU with a reducer includes a hydraulic motor section GU1 having a hydraulic motor M and this hydraulic motor section GU.
The rotation of the hydraulic motor M of No. 1 is input, and the crawler
It is composed of a reducer unit GU2 that reduces the rotation speed of the hydraulic motor and transmits the rotation to the sprocket SP that meshes with the CL. This hydraulic motor GU with a reducer has a casing CA of the reducer part GU2 attached to the vehicle body frame.
Installed on FL, crawler CL on sprocket SP
It is installed on a crawler vehicle by wrapping it around it.

In the motor unit GU1, a hydraulic motor M is provided in the casing CA, one end of which is attached to the vehicle body frame FL, and a ring gear L' of the reducer unit GU2 at the other end is rotatable with bearings B1 and B2. It is provided in

At the end of this casing CA, there is a switching valve FR1 for controlling the swash plate of the hydraulic motor M, which will be described later, and a counterbalance valve that controls the supply and discharge of pressure oil to the parking brake and cylinder block of the hydraulic motor M.
A flange portion FR to which a pipe for supplying and discharging pressure oil to the FR 2 and the hydraulic motor M, a pipe for discharging drain, etc. is attached is fixed.

The hydraulic motor M installed in the casing CA is connected to the carrier GU installed in the right end CA1 of the casing CA.
Bearing GU22 installed in 21 and flange FR
The shaft M1 is rotatably supported by the bearing FR3.
A cinder block M4 having a plurality of cylinders M2, M2... into which pistons M3, M3... are slidably fitted is installed, and this cylinder block M
In this configuration, a swash plate M5 is provided at a position where the four pistons M3, M3, . . . come into contact. The cylinder block M4 is connected to a counterbalance valve FR2 via a valve plate M6. Furthermore, a brake disc 62 is provided on the outer periphery of the cylinder block M4.
Parking brake M7 formed by piston 61
is provided. When pressure oil is supplied to the hydraulic chamber M63, the piston M61 of the parking brake M7 moves toward the flange FR to loosen the brake, and when the pressure oil in the hydraulic chamber M63 is discharged to the tank, the spring applies the brake. Press disk M62,
Apply braking force to the cylinder block. Note that this hydraulic chamber M63 is a counterbalance valve.
Connected to FR2, counterbalance valve FR2
When in the neutral position, the hydraulic chamber M63 is connected to the tank, and when in the switching position, the hydraulic chamber M63 is connected to the high pressure side of the main circuit.

The above hydraulic motor M is equipped with a counterbalance valve.
When FR2 is activated, pressure oil is supplied to and discharged from cylinder M2 of cylinder block M4 via valve plate M6, and also supplied to hydraulic chamber M63 of parking brake M7. Therefore, the parking brake force is released and the piston M3 is moved from the swash plate M
5, the cylinder block M4 rotates due to the reaction force, and the shaft M1 connected to this cylinder block M4 also rotates.

Note that the swash plate M5 is located below the center of the axis M1,
It is supported by two horizontally arranged spherical supports M52,
A cylinder M51 is provided at its upper end. This cylinder M51 is connected to the switching valve FR1,
Pressure oil is supplied and discharged from this switching valve FR1. When the switching valve FR1 is in the position shown, the pressure oil in the cylinder M51 is discharged and the swash plate M5 is in the position shown in FIG. 4. When the switching valve FR1 is operated, the cylinder M51 moves the tip of the swash plate M5, so the swash plate M5 rotates around the spherical receiver M52, reducing the inclination of the swash plate M5.

Therefore, when the swash plate M5 is in the illustrated position, the rotation of the hydraulic motor M is at a low speed and its torque is:
When the torque becomes high, pressure oil is supplied to the cylinder M51, and the inclination of the swash plate M5 becomes small, the hydraulic motor M
The rotation becomes high speed and its torque becomes low torque.

The reducer unit GU2 includes a ring gear L' rotatably supported by bearings B1 and B2 in the casing CA, and a bearing provided inside the ring gear L', and a bearing provided in the carrier GU21.
It is rotatably supported by the GU22 and a bearing GU25 provided on the lid GU23 fixed to the end face of the ring gear L, and is attached via the bearing GU26 to the eccentric shaft GU25 formed integrally with the shaft M1. A pin GU28' (see FIG. 2) fixed to the carrier GU21 passes through the wheel gear GU27.

As shown in FIG. 3, the ring gear L' is formed of a gear portion L1' and a flange portion L2'. The gear part L1' has a toothed part L12' formed therein, the wall thickness of which is approximately uniform, and a spigot part L14' that fits into the spigot part L15' of the flange part L2' and a welding part at the end thereof. Bevel L16'
(This groove L16' is the groove L1 of the flange portion L2'.
Matches 5'. ) is provided. Each of the pilot part L14' and the end part L13'', and the toothed part L12'
The intervals lT1 and lT2 are set to have substantially the same dimensions, and the thickness thereof is made uniform. Then, as shown in FIG. 1, in this ring gear L, after heat treatment (hardening treatment) is performed on the toothed part L12', the spigot part L14' is inserted into the spigot part L15',
After determining its position, it is formed by welding.

In addition, GU28 is the tooth profile L of the ring gear L'.
12'. and tooth profile L
The difference in the number of teeth between 12' and GU28 is 1 or more.
(1<L12'-GU28) In the above reduction gear unit GU2, when pressure oil is supplied to and discharged from the hydraulic motor M, and when the eccentric shaft GU25 is rotated, the wheel gear GU27 is connected to the eccentric shaft GU25.
Together with tooth profile part GU28 of wheel gear GU27
is caused to swing while being engaged with the toothed portion L12' of the ring gear L. Therefore, the eccentric shaft GU2
5 rotates once, the ring gear L is rotated by the difference in the number of teeth between the wheel gear and the ring gear.

In this embodiment, as explained above, the rotation of the hydraulic motor M drives the wheel gear of the reduction gear unit GU2.
The GU27 is oscillated, and the reduction ratio is obtained by dividing the difference in the number of teeth between the ring gear and the wheel gear by the number of teeth on the ring gear.

[Effect of idea]

In this invention, the ring gear is divided into a flange part and a gear part with a substantially uniform wall thickness, and after heat treatment is applied to the tooth profile part of this gear part, the positioning between the flange part and the gear part is determined. Since it has a welded structure, the distortion caused by heat treatment of the gear part can be kept to an extremely small value.Also, since the tooth profile part is an involute tooth profile, the distortion caused by heat treatment by welding etc. can be reduced to an extremely small value. , it can be absorbed by increasing or decreasing the backlash. Furthermore, since the other parts (other than the flange part and the toothed part of the foil) are not subjected to heat treatment, there is an advantage that there is no need for the process of reapplying after heat treatment as in the conventional method.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a hydraulic motor-equipped speed reducer according to an embodiment of the present invention, FIG. 2 is a cross-sectional view taken along line A-A in FIG. 1, and FIG. 3 is a partially enlarged view of FIG. 1. FIG. 4 is a partially enlarged view of a conventional reduction gear. (Same parts as in Figure 3.) M...Hydraulic motor, GU1...Reducer section, CA
...Casing, GU2...Hydraulic motor section, SP...
...Sprocket, GU25...Eccentric part, L'...Ring gear, GU27...Wheel gear, L
1'...Gear part, L2'...Flange part, L14'
...Pilot part, L15'...Pilot part.

Claims (1)

[Scope of utility model registration request] A ring gear having a flange to which a sprocket is attached is rotatably provided in a casing in which a hydraulic motor is provided, and an eccentric shaft driven by the hydraulic motor is rotatably attached to the ring gear. In a reduction gear with a hydraulic motor, the wheel gear is provided with a tooth profile that meshes with the tooth profile, and a pin fixed to the casing passes through the wheel gear, and the tooth profile of the wheel gear and ring gear is an involute tooth profile. The ring gear is divided into a flange portion and a gear portion having a substantially uniform wall thickness, and the toothed portion of the gear portion is heat treated, and then positioned between the gear portion and the flange portion, Ring gear of reducer in welded configuration.