JP2532760Y2 - Transmission device for hydraulically driven vehicle with upper swing type - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for an upper swing hydraulically driven vehicle, and more particularly to a transmission for an upper swing hydraulically driven vehicle capable of smoothly shifting gears.

[Conventional technology]

2. Description of the Related Art Conventionally, there is a technique described in Japanese Utility Model Laid-Open No. 56-93549 as a transmission for an upper turning hydraulically driven vehicle. This describes a power transmission device of an upper-slewing hydraulic drive vehicle equipped with a hydraulic motor that drives a hydraulic pump for supplying hydraulic oil to a hydraulic clutch and uses its own rotation as an input of a transmission. I have.

[Problems to be solved by the invention]

However, in the above conventional power transmission device, the hydraulic pump for supplying hydraulic oil to the hydraulic clutch is driven by a hydraulic motor that inputs rotation to a transmission, so that the hydraulic pump is switched to the hydraulic clutch regardless of the hydraulic motor. There is a problem that it is not possible to secure pressure oil for use. That is, for example, when traveling at an ultra-low speed with the rotation of the hydraulic motor lowered, the rotation speed of the hydraulic pump together with the hydraulic motor also decreases, so that the hydraulic clutch slips, and the hydraulic pump has a large discharge rate to prevent this slip. In the case of a hydraulic pump having a large discharge amount, there is a problem that an energy saving problem occurs.

[Means for solving the problem]

In order to solve the above problem, the transmission of a hydraulically driven vehicle according to the present invention, as described with reference to FIG. 1, is a traveling driven by hydraulic oil from a traveling hydraulic source A111 provided on an upper revolving superstructure. A hydraulic motor A11 for transmission and a transmission for shifting the rotation of the hydraulic motor A11 by switching the hydraulic clutches A13 and A14 are provided on the lower traveling body. A hydraulic motor A37 driven by pressure oil from a separately provided hydraulic source A32, and a hydraulic motor A37
And a hydraulic pump A38 driven by the hydraulic clutch A13 to supply pressure oil for switching to the hydraulic clutches A13, A14.

[Action]

According to the above configuration, the switching between the hydraulic clutches A13 and A14 is performed by the pressure oil from the hydraulic pump A38. This hydraulic pump A38 is driven by a hydraulic motor A37. This hydraulic motor A37 is driven by pressure oil from a hydraulic source A32. Thus, the hydraulic motor A driving the clutch hydraulic pump A38
Since the lower traveling body 37 is provided separately from the traveling hydraulic motor A11, the hydraulic power source A32 for driving the hydraulic motor A37 is provided.
The hydraulic motor A11 for traveling and the hydraulic pump A for clutches are provided on the upper revolving structure separately from the hydraulic source A111 for traveling.
And 38 are individually controlled. As a result, for example, even when the vehicle travels at an extremely low speed with the pressure oil from the hydraulic pressure source A111 for traveling reduced, the hydraulic pressure source A32 for the clutch is
The clutch hydraulic pump A38 can be driven via the clutch hydraulic motor A37 regardless of 111. Therefore, a predetermined amount of pressure oil for switching to the hydraulic clutches A13 and A14 can be secured.

〔Example〕

The embodiment will be described below with reference to FIGS. 1 and 2. An example machine equipped with this embodiment is a wheel-type upper swing hydraulic excavator. The transmission is, as shown in FIGS. 1 and 2,
It has an input shaft A12 and an output shaft A19, and the input shaft A12 is an external gear A12.
1, an external gear A131 that idles around the outer periphery of the input shaft A12, and a clutch A13 that separates the external gear A131 from the input shaft A12.
On the other hand, the output shaft A19, the external gear A191 that always meshes with the external gear A131, idles the outer periphery of the output shaft A19, and,
An external gear A141 that constantly meshes with the external gear A121, and an external gear A141
And a clutch A14 for separating the output shaft A19 from the
The gears are changed by changing the reduction ratio by disengaging any of the clutches A13 and A14. That is,
External gear A121 and external gear A141, and external gear A191 and external gear A1
Since the clutch 31 is always meshed with the clutch 31, the shift can be easily performed only by pressing one of the clutches A13 and A14, even if the vehicle is running. In this example,
If clutch A13 is crimped and clutch A14 is released,
When the vehicle travels at a low speed (first speed stage), on the other hand, when the clutch A14 is pressed and the clutch A13 is released, the vehicle travels at high speed (second speed stage).

Next, the transmission is as shown in FIG. First,
To describe the overall structure, the svel joint A35 in the center of the figure
On the left is the upper revolving superstructure, engine A30, hydraulic pumps A111 and A32, compressor A501, air tank A50,
A forward / reverse switching valve A112, a pilot switching valve A52, a connection circuit thereof, and a driver seat (not shown) are provided. On the other hand, hydraulic motors A11 and A37, the transmissions, hydraulic clutch operation switching valves (A40, A42, A43) and hydraulic pumps A38 and a connection circuit thereof are provided on the lower traveling body on the right side of the center svel joint A35 in the figure. Etc. are stored. Describing the configuration and operation, the hydraulic pump A32 driven by the engine A30, the hydraulic oil sucked from the oil reservoir,
It is sent to a hydraulic motor A37 via a circuit A36 passing through a swivel joint A35, and after being rotated, it is returned to an oil sump. The hydraulic pump A38 is directly connected to the hydraulic motor A37, is rotated by the hydraulic motor A37, and serves as a hydraulic source for supplying pressure oil to a main transmission control circuit in the lower traveling body. The hydraulic pump A38 supplies the hydraulic oil sucked from the oil reservoir A22 of the transmission case A10 via the strainer A21 to the circuit A39.
Then, oil is supplied to the clutch A13 or A14 of the transmission via the hydraulic clutch operation switching valve (A40, A42, A43) and the circuit A44 or A45, and the clutch A13 or A14 is disengaged. The surplus hydraulic oil is sent to the transmission as cooling and lubricating oil via the circuit A46. And the hydraulic clutch operation switching valve (A40, A4
2, A43) comprises a neutral valve A40, a fluid pressure gradually increasing valve A42, and a shift switching valve A43, and the arrangement order is also the order of the neutral valve A40, the fluid pressure gradually increasing valve A42, and the shift switching valve A43, Furthermore, a neutral valve
The A40 and the shift switching valve A43 are of a pilot type, and this pilot signal is guided from a pilot switching valve A52 provided in the driver's seat. Therefore, the pilot switching valve A52 of the pilot circuit, the neutral valve A40, and the shift switching valve
The relationship between A43 and the hydraulic clutches A13, A14 will be described. In this example, the pilot switching valve A52 is a manual type 3 position (H position, L position, N position) pilot pressure direction switching valve, and the neutral valve A40 is a spring / pilot type 2 position (HL position,
N)), and the shift valve A
Reference numeral 43 denotes a spring / pilot type two-position (H position, L position) clutch operating oil direction switching valve. Pilot switching valve A52
Is manually switched to the H position,
The pilot switching valve A52 shuts off compressed air from the air tank A50, and the pilot circuit A401 of the neutral valve A40.
And the pilot air pressure with the pilot circuit A56 of the shift switching valve A43 is drained to the outside, the neutral valve A40 is at the HL position, and
Move the shift switching valve A43 to the H position. In this case, this is the state shown in the figure, and the hydraulic oil sent from the hydraulic pump A38 via the circuit A39 reaches the HL position of the neutral valve A40, the fluid pressure gradually increasing valve A42, and reaches the speed changeover switching valve A43, and this speed change is performed. The hydraulic clutch A14 is crimped by the H position of the switching valve A43, while the hydraulic clutch A14 is pressed.
To release high-speed running. Also, pilot switching valve A5
2 is switched to the L position, the air tank A
The compressed air from 50 switches the speed changeover switching valve A43 via the pilot circuit A56 to the L position (at this time, the neutral valve A40 remains at the HL position). in this case,
The hydraulic oil from the hydraulic pump A38 reaches the shift switching valve A43 via the HL position of the neutral valve A40 and the fluid pressure gradually increasing valve A42, and presses the hydraulic clutch A13 by the L position of the shift switching valve A43,
On the other hand, the hydraulic clutch A14 is released for low-speed traveling. Further, when the pilot switching valve A52 is switched to the N position, the compressed air from the air tank A50 is sent to the neutral valve A40 via the pilot circuit A401, and the neutral valve A40 is switched to the N position. To That is, the hydraulic pump A38
Is shut off by the neutral valve A40 to the shift switching valve A43, so that no operating oil pressure is sent to the hydraulic clutch regardless of the position of the shift switching valve A43. As a result, traveling at this position becomes neutral (the vehicle stops). Incidentally, at the time of neutral, the escape path of the hydraulic pressure which has been acting on any of the hydraulic clutches up to that time is simultaneously operated with the neutral operation by the action of the fluid pressure gradually increasing valve A42 which will be described below. Transmission transmission sump A22
(Since the shift from low-speed running to high-speed running and the reverse shift are the same), it is possible to prevent the occurrence of the half-clutch state during shifting.
As shown in the figure, the fluid pressure gradually increasing valve A42 is provided with the neutral valve A40.
And a so-called modulation valve installed between the transmission and the speed changeover switching valve A43. Therefore, although there are various types, in this embodiment, a quick return type modulation valve which is a representative example is adopted. In the figure,
A421 is a quick return valve, and A422 is a modulation valve. When the clutch pressure A423 is low, the quick return valve A421 rapidly drains the clutch pressure A423 to the oil sump of the transmission by the spring force biased thereto, and as the clutch pressure A423 gradually increases, the oil of the transmission The operation is such that the drain is stopped in the reservoir and the hydraulic pressure generated by the modulation valve A422 is gradually increased to the relief pressure (this operation and the configuration are also shown in the circuit of the figure). On the other hand, the modulation valve A422 obtains the action of the quick return valve A421, and has an action of gradually bringing the clutch pressure A423 to the relief pressure as the clutch pressure A423 increases (that is, an action capable of preventing a shift shock) and configuration. (The operation and configuration are also shown in the circuit of FIG. 3). In addition, the relief hydraulic fluid is
It is sent to the clutch portion and the bearing portion of the transmission via A46, and cools and lubricates them (that is, the transmission can be appropriately lubricated).

Finally, summarizing the above and describing the effects of the embodiment, the hydraulic motor A37 and the hydraulic pump A38 can be installed in a pair at the same place, and furthermore, the hydraulic pump A38 and the oil sump A of the transmission can be installed.
Since the hydraulic circuit including the hydraulic switching clutch 22 and the hydraulic clutch operation switching valve A42 is modularized, the transmission control circuit can be made compact. As a result, maintenance and inspection could be easily performed simply by attaching and detaching this module. Furthermore, since this example is a hydraulically driven vehicle equipped with a hydraulic swivel A35, each device of the upper revolving unit and the lower traveling unit can be connected with only two circuits A36 and A36, and the configuration is simple. Was completed. More specifically, as described above, it is possible not only to prevent the occurrence of a shift shock, but also to use the surplus of the working oil for the clutch as necessary for cooling and lubricating the transmission. The function of the fluid pressure gradually increasing valve A42 could be maximized by the arrangement order of the valves, and the transmission control could be made more efficient. Furthermore, since the pilot type is used, the driver can operate the pilot shift valve A32 to control the main shift control circuit provided at a distant place and freely change gears, thereby reducing driver fatigue. The reduction was achieved.

According to the above embodiment, the hydraulic motor A37 is provided on the lower traveling body separately from the hydraulic motor A11, and the hydraulic source A32 for driving the hydraulic motor A37 is provided on the upper revolving body separately from the hydraulic source A111. , Hydraulic motor A11 and hydraulic pump A38
And can be individually controlled. Therefore, for example, even when the vehicle travels at an extremely low speed while reducing the pressure oil from the hydraulic pressure source A111, the hydraulic pressure source A32
Can drive the hydraulic pump A38 via the hydraulic motor A37 irrespective of the hydraulic source A111, so that a predetermined amount of pressure oil for switching to the hydraulic clutches A13 and A14 can be secured. As a result, an optimal amount of pressure oil for switching to the hydraulic clutches A13 and A14 can be always secured, and the hydraulic pump A38 does not need to have a discharge amount larger than necessary, which can contribute to energy saving.

[Effect of the invention]

As is clear from the description of the above-described embodiment, the present invention takes measures described in the claims of the utility model registration, if necessary. Even when the vehicle travels at a low speed, the hydraulic source A32 can drive the hydraulic pump A38 via the hydraulic motor A37 regardless of the hydraulic source A111, so that a predetermined amount of hydraulic oil for switching to the hydraulic clutches A13 and A14 can be secured. As a result, the hydraulic clutches A13, A
The optimal amount of pressure oil for switching to 14 can always be ensured, and the hydraulic pump A38 does not need to have an unnecessarily large discharge amount, which can contribute to energy saving.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram according to an embodiment, and FIG. 2 is a schematic sectional view of a transmission used in the embodiment. A32… Hydraulic pump A37… Hydraulic motor A38 …… Hydraulic pump A40 …… Neutral valve A42 …… Fluid pressure gradually increasing valve A43 …… Shift switching valve A52 …… Pilot switching valve

Claims (1)

(57) [Scope of request for utility model registration] 1. A traveling hydraulic motor A11 driven by hydraulic pressure from a traveling hydraulic power source A111 provided on an upper-part turning body, and a shift for changing the rotation of the hydraulic motor A11 by switching hydraulic clutches A13 and A14. In a transmission for an upper swing type hydraulically driven vehicle having a lower traveling body and a hydraulic motor A driven by pressure oil from a hydraulic source A32 separately provided in the upper swing body
37, and a hydraulic pump A38 driven by the hydraulic motor A37 to supply pressure oil for switching to the hydraulic clutches A13, A14.
The transmission device for an upper swing hydraulically driven vehicle, comprising: